WO2019019553A1 - 一种洗衣机阻尼结构及设计方法、横向减震装置及洗衣机 - Google Patents

一种洗衣机阻尼结构及设计方法、横向减震装置及洗衣机 Download PDF

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Publication number
WO2019019553A1
WO2019019553A1 PCT/CN2017/119726 CN2017119726W WO2019019553A1 WO 2019019553 A1 WO2019019553 A1 WO 2019019553A1 CN 2017119726 W CN2017119726 W CN 2017119726W WO 2019019553 A1 WO2019019553 A1 WO 2019019553A1
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WIPO (PCT)
Prior art keywords
section
damping
washing machine
diameter
rod
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Application number
PCT/CN2017/119726
Other languages
English (en)
French (fr)
Inventor
张江涛
武凤玲
牟秋启
范强
国强
劳春峰
Original Assignee
青岛海尔洗衣机有限公司
青岛海尔智能技术研发有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Priority claimed from CN201710632488.3A external-priority patent/CN109306600B/zh
Priority claimed from CN201710630276.1A external-priority patent/CN109306599B/zh
Priority claimed from CN201710632489.8A external-priority patent/CN109306601B/zh
Application filed by 青岛海尔洗衣机有限公司, 青岛海尔智能技术研发有限公司 filed Critical 青岛海尔洗衣机有限公司
Publication of WO2019019553A1 publication Critical patent/WO2019019553A1/zh

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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

Definitions

  • the invention belongs to the technical field of washing machines, and particularly relates to a damping structure and design method of a washing machine, a lateral damping device and a washing machine.
  • the vibration reduction of the washing machine mainly suspends the inner and outer barrels of the washing machine by hanging the hanging rods at the four corners of the washing machine.
  • the inner and outer barrels are all reduced by the compression boom, and the boom absorbs the inner and outer cylinders by its own damping. vibration.
  • the use of the boom can only buffer the vibration in the vertical direction, and can not reduce the lateral vibration, resulting in the collision of the box under the large eccentricity, affecting the volume ratio and starting ability of the washing machine.
  • the rotation speed is increased from zero to 700 rpm or even higher.
  • the eccentric load caused by the unbalance of the clothes gradually increases with the increase of the rotational speed, and the fundamental frequency of the excitation force corresponding to the eccentric load increases from zero to ten Hz.
  • the pulsator washing machine generally has a distinct natural mode around 1 to 3 Hz. When the washing machine speed passes its modal frequency, it will cause resonance phenomenon in the washing machine. If the resonance phenomenon of the washing machine cannot be well controlled, the washing machine may be damaged or damaged.
  • the spring is fixed between the outer cylinder and the box in the patent CN201020229971.0 to provide the restoring force.
  • the resonance occurs, there is a large displacement between the outer cylinder and the casing, so that the spring connecting the outer cylinder and the casing is stretched or compressed to generate a restoring force, and the displacement between the outer cylinder and the casing is reduced.
  • the spring transmits the vibration on the outer cylinder to the box, causing the vibration of the washing machine box to sound and the noise of the whole machine to rise.
  • the invention aims at the above problems existing in the prior art, and provides a damping structure of a washing machine, which can prevent the washing machine from colliding with a box at a low speed dehydration, and can ensure that the vibration transmitted to the box is not increased when the water is dehydrated at a high speed. As a result, the noise of the whole machine increases.
  • a washing machine damping structure comprises a guiding sleeve and a guiding rod extending from one end into the guiding sleeve, wherein the inner side of the guiding sleeve is provided with a damping piece which cooperates with the guiding rod to generate a damping force, and the guiding rod has a central hollow a carrying section, and a working section at both ends of the empty section, the diameter of the empty section is smaller than the inner diameter of the damping piece, and the diameter of the working section is larger than the inner diameter of the damping piece; when the washing machine is stably operated, the The idle section is located at the damper sheet; when the vibration of the outer cylinder of the washing machine is large, the working section is located at the damper sheet.
  • the working section has a cylindrical main working section, and a variable diameter section disposed between the empty section and the main working section, and the diameter of any section of the variable section is located in the Between the no-load segment diameter and the working segment diameter.
  • the guiding rod further has a cut-off section extending toward the end portion along the working section, the guiding rod is telescopically moved relative to the guiding sleeve, when the cut-off section of the guiding rod moves to the vicinity of the damping piece The relative movement of the person stops.
  • the guiding sleeve is a cylindrical structure with one end open, the damping piece is disposed inside the open end of the guiding sleeve, and the other end of the guiding sleeve is provided with a first hinge portion.
  • the guiding rod is a hollow rod having an opening at one end, the open end of which is located in the guiding sleeve, and the other end of the guiding rod is provided with a second hinge portion.
  • a ferrule is disposed between the damper sheet and the guide sleeve, and an annular first slot is opened on an inner side of the open end of the guide sleeve, the ferrule is located at the first slot;
  • the inner side of the sleeve is provided with a second slot, and the damping piece is located at the second slot and is in contact with the radial edge of the first slot.
  • end of the ferrule is further provided with a rib extending outward in the radial direction, the rib being located at an end of the open end of the guiding sleeve.
  • At least two buckles are arranged on the outer side of the ferrule, and the first slot is provided with a card slot matched with the buckle, and the buckle is fastened to the card. Inside the slot.
  • a vent hole is formed in the wall of the opposite end of the open end of the guide sleeve.
  • the present invention also provides a design method of the above damping structure, the design method comprising the following steps:
  • the length L z of the idle section of the guide rod is determined
  • L Max E The minimum spacing between the guide bar length L z load segment, and the outer tube and the housing, the guide rod determining the working length L w;
  • step A there is step A3 after step A2, and the positive pressure between the working section of the guiding rod and the damping piece is determined according to the damping force of the damping structure being F D and the friction coefficient c of the selected damping piece.
  • F N F D /c.
  • step A there is a step A4 after step A3, and according to the positive pressure F N and the equivalent stiffness k c of the damping piece, the working section between the working rod and the damping piece is determined.
  • the span spacing d c F N /k c .
  • a working portion of the guide rod has a frustum-shaped transition between the maximum diameter ⁇ w of the working section and the diameter ⁇ z of the idle section.
  • a working area maximum diameter ⁇ w of the guiding rod and a curved surface transition angle ⁇ z have a curved transition section, and a diameter of any cross section of the curved transition section is located in the The working section has a maximum diameter ⁇ w and a diameter of the idle section ⁇ z .
  • the working section maximum diameter ⁇ w of the guiding rod and the empty section diameter ⁇ z have at least one cylindrical transition section, and the diameter of the cylindrical transition section is located at the working section of the guiding rod Between the diameter ⁇ w and the diameter of the idle section ⁇ z .
  • the present invention also provides a washing machine having the damping structure, which can prevent the washing machine from colliding with the box at low speed dehydration, and can ensure that the vibration transmitted to the box is not increased when the high speed dehydration is performed. Large, resulting in increased noise.
  • a washing machine comprising a box body and an outer tube and an inner tube disposed in the box body, wherein the outer tube is hoisted on the box body by a boom, and the outer tube, the box body and the hanging rod are three
  • the above damping structure is provided between any two of them.
  • Another object of the present invention is to provide a washing machine lateral damping device having the above damping structure, comprising a first mounting seat hinged to one end of the damping structure, and a vertically disposed sliding rod, the other end of the damping structure being The sliding sleeve is disposed on the sliding bar, and the two ends of the sliding bar are respectively provided with a second mounting seat.
  • a sliding hole is defined in the damping structure, the sliding rod passes through the sliding hole, and a second cushion is disposed between the sliding rod and the sliding hole.
  • the second cushion comprises a second cylindrical body, a second flange extending outward along the upper and lower ends of the second cylindrical body, and the two second and second tubular bodies A receiving groove is formed that matches the edge of the slide hole.
  • two upper and lower limiting grooves are disposed on the sliding bar, and the sliding holes slide between the two limiting grooves on the sliding bar.
  • the first mounting seat is provided with a pin shaft
  • the damping structure is provided with a pin hole matched with the pin shaft
  • a first cushion pad is disposed between the pin shaft and the pin hole.
  • the first mounting seat has two mounting plates disposed in parallel, and the two mounting plates are respectively disposed opposite to each other, and the pin holes are located between the two pin seats.
  • a pin hole is formed in the pin seat, and the pin passes through the pin hole.
  • the damping structure includes a guiding rod and a guiding sleeve sleeved outside the guiding rod, and the inner side of the guiding sleeve is provided with a damping piece that cooperates with the guiding rod to generate a damping force, and the guiding rod has a central hollow And a working section at both ends of the empty section, the diameter of the empty section is smaller than the inner diameter of the damping piece, and the diameter of the working section is larger than the inner diameter of the damping piece.
  • one end of the guiding rod is located in the guiding sleeve, and the other end is set on the sliding rod;
  • the guiding sleeve is a cylindrical structure with one end open, and the other end is hinged with the first mounting seat.
  • the working section has a cylindrical main working section, and a variable diameter section disposed between the empty section and the main working section, and the diameter of any section of the variable section is located in the Between the no-load segment diameter and the working segment diameter.
  • the guiding rod further has a cut-off section extending along the working section toward the end, the guiding rod is telescopically moved relative to the guiding sleeve, when the cut-off section of the guiding rod moves to the damping piece The relative movement of the person stops.
  • a ferrule is disposed between the damper sheet and the guide sleeve, and an annular first slot is opened on an inner side of the open end of the guide sleeve, the ferrule is located at the first slot;
  • a second slot is defined in the inner side of the slot, and the damper sheet is located at the second slot and is in contact with the radial edge of the first slot.
  • end of the ferrule is further provided with a rib extending outward in the radial direction, the rib being located at an end of the open end of the guiding sleeve.
  • the outer side of the ferrule is axially arranged with at least two buckles, and the first notch is provided with a card slot matched with the buckle, and the buckle is located in the card slot.
  • a vent hole is formed in the wall of the opposite end of the open end of the guide sleeve.
  • the damping structure provided by the invention is used for providing a damping force in a horizontal direction.
  • the variable damping force is provided to vibrate in the outer cylinder.
  • the damping structure gives sufficient damping force to prevent the outer cylinder from colliding with the box; and in the safe amplitude of the outer cylinder of the washing machine, the damping structure gives less damping force or no damping force; thus, the washing machine runs stably.
  • the idle section is located at the damper sheet; when the vibration of the outer cylinder of the washing machine is large, the working section is located at the damper sheet; this can prevent the washing machine from colliding with the box at low speed dehydration, and can It ensures that the high-speed dehydration will not increase the noise of the whole machine due to the increase of the vibration transmitted to the cabinet.
  • FIG. 1 is a schematic structural view of an embodiment of a damping structure proposed by the present invention
  • Figure 2 is a cross-sectional structural view of Figure 1;
  • Figure 3 is an enlarged exploded view of the damper sheet of Figure 2;
  • Figure 4 is a schematic structural view of the damper rod of Figure 2;
  • Figure 5 is a washing machine provided with the damping structure of Figure 1;
  • Figure 6 is a flow chart of a method of designing a damping structure
  • Figure 7 is a schematic view showing a specific structure of the guide rod
  • FIG. 8 is a schematic structural view of an embodiment of a lateral shock absorbing device for a washing machine according to the present invention.
  • Figure 9 is a schematic enlarged view of the area A of Figure 8.
  • Figure 10 is a cross-sectional structural view of Figure 8.
  • Figure 11 is an enlarged schematic structural view of a region B in Figure 10;
  • Figure 12 is a schematic enlarged view of the area C of Figure 10;
  • Figure 13 is an enlarged schematic view showing a region D in Figure 10;
  • Figure 14 is a first specific structural diagram of the guide rod
  • Figure 15 is a third specific structural schematic view of the guide rod
  • the washing machine comprises a casing 10, a set outer cylinder 20 and an inner cylinder 30 disposed in the casing 10, and the outer cylinder 20 passes through four
  • the boom 40 is hoisted on the corner plate of the four corners of the box body 10; the washing machine crash box mainly occurs in the dehydration start phase, when the base frequency of the excitation force corresponding to the washing machine speed is close to the common frequency of the internal and external barrel crane boom forming system,
  • the inner and outer cylinders resonate, and the amplitude of the outer cylinder 20 is significantly increased, thereby causing the outer cylinder 20 to collide with the casing and causing a collision box.
  • the damping structure 50 is disposed in the casing 10, the outer cylinder 20, and the boom 40. Between the two, it is preferably disposed between the casing 10 and the outer cylinder 20. Due to the relative staticness of the casing 10, a more effective damping force can be provided to avoid the collision of the bucket.
  • the damper structure 50 includes a guiding rod 1 and a guiding sleeve 3 which is disposed outside the guiding rod 1.
  • a damping piece 2 is provided which cooperates with the guiding rod 1 to generate a damping force
  • the guiding rod 1 has The idle section 12 in the middle and the working section 11 at both ends of the idle section 12, wherein the diameter of the idle section 12 is smaller than the inner diameter of the damper sheet 2, and the diameter of the working section 11 is larger than the inner diameter of the damper sheet 2.
  • a damping force is generated between the guide rod 1 and the damper sheet 2 to avoid the collision of the bucket; the guide rod 1 has the idle section 12 and the working section 11, and when the washing machine is stably operated, the idle section 12 is located in the damping At the sheet 2, that is, within the safe amplitude of the stationary operation of the washing machine outer cylinder 20, the damping structure imparts a small damping force or no damping force, and thus the vibration on the outer cylinder 20 cannot be transmitted to the casing 10 through the damping structure 50.
  • the increase of the noise is avoided; when the vibration of the outer cylinder of the washing machine is large, there is a risk of hitting the barrel.
  • the expansion and contraction of the guide rod 1 is also relatively large, and the working section 12 is located at the damper sheet 2, and the prevention occurs outside.
  • the damping force of the vibration of the cylinder 20 is such that the vibration amplitude of the outer cylinder 20 is reduced to avoid hitting the barrel; that is, the damping structure 50 provides a variable damping force, and the damping structure 50 needs to prevent the washing machine from colliding at a low speed dehydration. It can also ensure that the noise of the whole machine will not increase due to the increase of the vibration transmitted to the box when the high-speed dehydration is performed.
  • the idle section 12 is cylindrical
  • the working section 11 has a cylindrical main working section 111 and a variable diameter section 112 disposed between the idle section 12 and the main working section 111.
  • the portion of the variable diameter section 112 having a diameter larger than the inner diameter of the damper sheet 2 is in contact with the damper sheet 2 to generate a damping force;
  • the variable diameter section 112 is in the shape of a truncated cone, that is, the busbar of the variable diameter section 112 is connected to the idle section 12 and A straight line inclined at one end between the main working sections 111, and the diameter of any section of the variable diameter section 112 is located between the diameter of the idle section 12 and the diameter of the main working section 111.
  • the guide rod 1 can smoothly transition between the idle section 12 and the working section 11 during the telescopic movement, and the variable diameter section 112 passes between the variable diameter section 112 and the damping piece 2 when the variable diameter section 112 passes through the damping piece 2.
  • the damping force gradually changes.
  • the guiding rod 1 further has a cut-off section 13 extending along the working section 11 toward the end.
  • the diameter of the cut-off section 13 is definitely larger than the diameter of the working section 11, and the guiding rod 1 is telescopically moved relative to the guiding sleeve 3, when the guiding rod
  • the cut-off section 14 of 1 moves to the vicinity of the damper sheet 2, the relative motion of both stops.
  • the guide rod 1 can be prevented from coming off the guide sleeve 3, and only when the amplitude of the outer cylinder 20 is large, the cut-off section 13 can also move to the vicinity of the damper sheet 2, at which time the guide rod 1 and the guide sleeve 3 are relatively stationary. That is, the two form a rigid whole, which can give the outer cylinder 20 a rigid blocking force and prevent the outer cylinder 20 from colliding with each other.
  • the guide sleeve 3 is a cylindrical structure with one end open, the damping piece 2 is disposed inside the open end of the guide sleeve 3, and the other end of the guide sleeve 3 is provided with a first hinge portion 31.
  • the vibration of the outer cylinder 20 drives the guiding rod 1 to move relative to the guiding sleeve 3 to provide a variable damping force;
  • the vent hole 32 is formed in the sleeve wall at the opposite end of the opening end of the guiding sleeve 3, and the guiding rod 1 is in the guiding sleeve 3
  • gas can flow out through the vent 32 or into the guide sleeve 3, avoiding the free end of the guide rod 1 enclosing a gas in the guide sleeve 3, so that the gas in the guide sleeve 3 can be moved when the guide rod 1 moves It flows out or is replenished so that when the vibration of the outer cylinder 20 is slow, gas damping is not formed.
  • the guiding rod 1 is a hollow rod having an opening at one end, the open end of which is located in the guiding sleeve 3, and the hollow rod of the guiding rod 1 is arranged, and the chamber of the guiding rod 1 is connected with the chamber of the guiding sleeve 3. In this way, a large receiving space is formed, and when the guiding rod 1 telescopically moves in the guiding sleeve 3, the influence of the airflow flowing through the through hole 32 on the guiding rod 1 is reduced; and the other end of the guiding rod 1 is provided with the second hinge Part 14.
  • a ferrule 5 is disposed between the damper sheet 2 and the guide sleeve 3, and an annular first notch 33 is opened inside the open end of the guide sleeve 3, and the ferrule 5 is provided.
  • the damper sheet 2 is fixed by the ferrule 5 and the first notch 33, and the thickness of the ferrule 5 is equal to the thickness of the first notch 33, so that the connection fixing structure at both ends of the damper sheet 2 is ensured to be flush;
  • the thickness of 2 is greater than the thickness of the second notch 51, that is, a portion of the damper sheet 2 projects inwardly, and the working portion of the guide bar 1 moves relative to the convex portion of the damper sheet 2 to generate a frictional damping force.
  • At least two buckles 52 are arranged on the outer side of the ferrule 5, and the first slot 33 is provided with a card slot 331 matching the buckle 52, and the buckle 52 is affixed.
  • the plurality of buckles 52 are evenly disposed in the axial direction of the ferrule 5; thus, by providing the buckle 52 and the card slot 331, the fixing between the ferrule 5 and the guide sleeve 3 is enhanced. Sex, while making the assembly operation of the ferrule 5 simple.
  • a rib 53 extending radially outward is further provided at the end of the ferrule 5, and the rib 53 is located at the end of the open end of the guide sleeve 3.
  • the design of the damping structure 50 needs to be performed for a specific washing machine model, and the main structure of the damping structure 50 designed for the washing machine is derived according to the known conditions of the washing machine.
  • the parameters ensure that the damping structure 50 has the above-described effects.
  • the design method of the damping structure 50 in this embodiment includes the following steps:
  • the dehydration start eccentric mass m e of the washing machine is determined; the highest resonance frequency f PMax of the low-frequency rigid body mode of the washing machine is a value simulated under ideal conditions; the calculated eccentric force Fe The maximum eccentric force when dehydrating the washing machine.
  • the anti-collision box device 50 needs to provide the anti-collision box balance force F C , wherein F C >F e -F h -F a is required .
  • F h is the horizontal balance force provided by the boom 40
  • F a is the elastic restoring force provided by the motor shaft.
  • F h is related to the deformation amount of the spring of the boom 40 and the angle between the boom 40 and the vertical direction
  • F a is related to the deviation angle of the motor shaft. Since F h is usually small and F a is related to the main shaft yaw angle, these two forces are replaced by the safety factor s1.
  • each washing machine is guaranteed to have at least two or more anti-collision box devices 50, and each washing machine at least guarantees two anti-collision box devices placed in different directions to ensure that when the outer tube 20 vibrates in the horizontal direction,
  • the crash box device 50 dampens the vibration of the outer cylinder 20 from two directions.
  • the number of crash box devices 50 is recommended to be an integer multiple of 2, preferably 2, 4, 6, 8.
  • the angle between the adjacent two anti-collision box devices 50 on the horizontal plane is between 30° and 150°, preferably four anti-collision box devices 50 are used, and the adjacent two anti-collision box devices 50 are perpendicular to each other. That is, the angle between the adjacent two crash box devices 50 on the horizontal plane is 90°.
  • the damper sheet 2 is circular
  • ⁇ c is the inner diameter of the damper sheet 2
  • the maximum diameter ⁇ w of the working section 11 of the guide rod 1 and the inner diameter ⁇ c of the damper sheet 2 need to be selected to a value, and Calculate another.
  • the diameter ⁇ z of the idle section 12 of the guide rod 1 is determined according to the inner diameter ⁇ c of the damper sheet 2.
  • the displacement amplitude d O is a displacement amplitude in the horizontal direction
  • s 4 is a safety factor
  • s 4 > 1 to ensure that the outer cylinder 40 is In stable operation
  • the idle section 12 is located at the damper sheet 2, and the damper structure 50 does not provide a damping force; wherein, 1 ⁇ s 4 ⁇ 3, but the value of s 4 cannot be too large, and the vibration amplitude of the outer cylinder 20 of the washing machine is avoided.
  • the working section of the guide bar 1 is not at the damper sheet 2, preferably, 1 ⁇ s 4 ⁇ 1.5.
  • L Max E The minimum spacing between the guide rod length L z idling section 1, and the outer cylinder 20 and the housing 10, determine the length L w guide rod 11 of the working section.
  • the working length of the guide rod is L w ⁇ L Max - L z /2, wherein L Max is the minimum distance between the outer cylinder and the casing.
  • L Max is the minimum distance between the outer cylinder and the casing.
  • the rigidity of the outer cylinder 20 is such that the impingement of the outer cylinder 20 is avoided, and thus the length of the guide rod working section L w ⁇ L Max - L z /2 is set.
  • the maximum diameter ⁇ w of the working section 11 of the guiding rod 1 is: the maximum diameter ⁇ w of the working section 11 of the guiding rod 1 , the working section length L w , the diameter of the idle section 12 ⁇ z , and the length of the idle section 12 L z , the inner diameter ⁇ c of the damper sheet 2.
  • a specific structural form of the guide rod 1 is an equal diameter cylindrical section having a diameter of ⁇ z and a length L z
  • the working section 11 has an equal diameter cylindrical section 111 having a diameter of ⁇ w
  • the frustum-shaped transition section 112 the diameter of any cross-section of the frustum-shaped transition section is located between the maximum diameter ⁇ w of the working section 11 of the guide rod 1 and the diameter ⁇ z of the idle section 13 .
  • the truncated cone transition section 112 is a frustum between the equal diameter cylindrical section 111 and the idle section 12, the cutoff section 13 is located at both ends of the guide rod 1, and the cutoff section 13 is also an equal diameter cylindrical section.
  • the design process is illustrated by taking the 8kg platform pulsator washing machine as an example.
  • the design method is as follows:
  • FIG. 3 to 8 and FIG. 13 are an embodiment of a lateral damper device for a washing machine according to the present invention.
  • the washing machine includes a casing 10, a set of outer cylinders 20 disposed in the casing 10, and The inner cylinder 30 and the outer cylinder 20 are hoisted on the corner plates of the four corners of the casing 10 through four booms 40; the washing machine crash box mainly occurs in the dehydration start phase, when the washing machine speed corresponds to the excitation force fundamental frequency and the inner and outer barrel machine When the common frequency of the boom forming system is close, the inner and outer cylinders resonate, and the amplitude of the outer cylinder 20 is significantly increased, thereby causing the outer cylinder 20 to collide with the casing and the collision box is generated.
  • the lateral damper 50 is disposed on the casing 10, the outer cylinder 20, and the boom 40. Between the two of the three, it is preferably disposed between the casing 10 and the outer cylinder 20. Due to the relative staticness of the casing 10, a more effective damping force can be provided to avoid the collision of the bucket.
  • the washing machine lateral damper device 50 includes a damping structure including a guiding rod 1, and a guiding sleeve 3 fitted on the outside of the guiding rod 1, in the guiding sleeve 3
  • the inner side is provided with a damping piece 2 that cooperates with the guide rod 1 to generate a damping force.
  • a first mounting seat 6 is hinged at one end of the damping structure, and the other end of the damping structure is slidably fitted on the sliding rod 7.
  • the sliding rod 7 is vertically disposed, and a second mounting is respectively disposed at both ends of the sliding rod 7.
  • One end of the damping structure can be slid on the sliding rod 7, so that when the outer cylinder 20 has vibration in the up and down direction, the damping structure can be horizontally or approximately horizontally slid by sliding on the sliding rod 7, so that the damping structure is mainly
  • the force used to dampen the horizontal direction is beneficial to increase the effect of the lateral damping and avoid the impact of the box caused by the excessive amplitude of the outer cylinder.
  • the first mounting seat 6 is fixed on the outer cylinder 20, and the two second mounting seats 8 are fixed up and down on the casing 10; when the outer cylinder 20 vibrates, the first mounting seat 6 and One end of the damper structure follows the outer cylinder 20 to vibrate.
  • the vibration at any point on the outer cylinder 20 can be decomposed into vibrations in the up-and-down direction, the left-right direction, and the front-rear direction, wherein the vibrations in the left-right direction and the front-rear direction are horizontal vibrations.
  • both ends of the damping structure have a certain distance in the up and down direction, and at this time, the other end of the damping structure slides on the sliding rod 7, and tends to dampen the structure level.
  • the direction of movement Since the casing 10 is in a relatively static state, the second mounting seat 8 is fixed on the casing 10, which ensures that the sliding rod 7 is in a vertical state, which is advantageous for ensuring smooth sliding of the other end of the damping structure on the sliding rod 7.
  • one end of the guiding rod 1 is located in the guiding sleeve 3, and the other end of the guiding rod 1 is provided with a sliding hole 14 and is fitted on the sliding rod 7.
  • the slide bar 7 passes through the slide hole 14 and a second cushion pad 9 is provided between the slide bar 7 and the slide hole 14.
  • the rigid contact between 14 avoids noise between the sliding rod 7 and the sliding hole 14 during sliding and when the damping structure is stressed; and when the damping structure is not in the horizontal plane, that is, both ends of the damping structure are up and down
  • the direction has a certain distance.
  • the axis of the sliding hole 14 coincides with the axial portion of the sliding rod 7.
  • the portion of the second cushioning pad 9 is elastically deformed by pressing, and the pulling force in the up and down direction is generated in the damping structure, so that the sliding The hole 14 can move smoothly.
  • the second cushion 9 includes a second cylindrical body 91, a second flange 92 extending outward along the upper and lower ends of the second cylindrical body 91, and two second turns.
  • the side 92 and the second cylindrical body 91 form a receiving groove that matches the edge of the sliding hole 14; and when the sliding hole 14 moves on the sliding bar 7, the second buffering is caused by the blocking of the upper and lower flanges 92.
  • the pad 8 snaps over the edge of the slide hole 14 and moves together.
  • two upper and lower limiting grooves 71 are provided on the sliding rod 7, and the sliding holes 14 slide between the two limiting grooves 71 on the sliding rod 7.
  • the limiting groove 71 By setting the limiting groove 71, the range of movement of the sliding hole 14 on the sliding rod 7 is defined, and the sliding smoothness of the sliding hole 14 on the sliding rod 7 is ensured to avoid the jamming situation.
  • the guide sleeve 3 is a cylindrical structure with one end open, the damping piece 2 is disposed inside the open end of the guide sleeve 3, and the other end of the guide sleeve 3 is provided with a pin hole 31, And hinged with the first mount 6.
  • a pin 61 is disposed on the first mounting seat 6, the pin 61 is vertically disposed, the guiding rod 1 is rotatable around the pin 61, and a first cushion is disposed between the pin 61 and the pin hole 31, and the first cushion is provided.
  • the same structure as the second cushion 9 is employed.
  • the first mounting seat 6 has two mounting plates 63 arranged in parallel, and the two mounting plates 63 are respectively provided with pin seats 62 adjacent to each other, and the pin holes 31 are located between the two pin seats 62.
  • a pin hole 64 is formed in the pin holder 62, and the pin 61 passes through the pin hole 64.
  • the guiding rod 1 when the outer cylinder 20 vibrates, the guiding rod 1 is moved relative to the guiding sleeve 3 to provide a variable damping force; the vent hole 32 is opened on the opposite end wall of the opening end of the guiding sleeve 3, and the guiding rod 1 is disposed on the guiding rod 1
  • the gas can flow out through the vent hole 32 or into the guide sleeve 3, and the free end of the guide rod 1 is prevented from enclosing a gas in the guide sleeve 3, so that the guide sleeve 1 moves when the guide rod 1 moves.
  • the gas in 3 can flow out or be replenished so that no gas damping is formed when the vibration of the outer cylinder 20 is slow.
  • the guiding rod 1 has a middle idle section 12 and a working section 11 at both ends of the idle section 12, wherein the diameter of the idle section 12 is smaller than the inner diameter of the damping piece 2, and the working section The diameter of 11 is larger than the inner diameter of the damper sheet 2.
  • the damping force is generated between the guiding rod 1 and the damping piece 2 to avoid the collision of the bucket; the guiding rod 1 has the idle section 12 and the working section 11, and when the washing machine is stably operated, the idle section 12 is located at the damping piece 2, That is, in the safety amplitude of the outer cylinder 20 of the washing machine in a stable operation, the lateral damper device gives a small damping force or does not give a damping force, so that the vibration on the outer cylinder 20 cannot be transmitted to the casing 10 through the lateral damper device 50. The noise is prevented from increasing; when the vibration of the outer cylinder of the washing machine is large, there is a risk of hitting the barrel.
  • the stretching range of the guiding rod 1 is also relatively large, and the working section 12 is located at the damping piece 2, and the outer tube is prevented at this time.
  • the damping force of the vibration causes the vibration amplitude of the outer cylinder 20 to be reduced to avoid the collision of the bucket; that is, the lateral damping device 50 provides a variable damping force, and the lateral damping device 50 needs to prevent the washing machine from colliding at low speed dehydration.
  • the box problem can ensure that the high-speed dehydration will not increase the noise of the whole machine due to the increase of the vibration transmitted to the box.
  • the idle section 12 is cylindrical, and the working section 11 has a cylindrical main working section 111 and a variable diameter section 112 disposed between the idle section 12 and the main working section 111.
  • the variable diameter section 112 The portion having an upper diameter larger than the inner diameter of the damper sheet 2 is in contact with the damper sheet 2 to generate a damping force; the variable diameter portion 112 is in the shape of a truncated cone, that is, the bus bar of the variable diameter portion 112 is connected to the idle portion 12 and the main working portion 111.
  • a straight line with one end inclined, the diameter of any section of the variable diameter section 112 is located between the diameter of the idle section 12 and the diameter of the main working section 111.
  • the guide rod 1 can smoothly transition between the idle section 12 and the working section 11 during the telescopic movement, and the variable diameter section 112 passes between the variable diameter section 112 and the damping piece 2 when the variable diameter section 112 passes through the damping piece 2.
  • the damping force gradually changes.
  • the guiding rod 1 further has a cut-off section 13 extending along the working section 11 toward the end.
  • the diameter of the cut-off section 13 is definitely larger than the diameter of the working section 11, and the guiding rod 1 is telescopically moved relative to the guiding sleeve 3, when the guiding rod
  • the cut-off section 14 of 1 moves to the vicinity of the damper sheet 2, the relative motion of both stops.
  • the guide rod 1 can be prevented from coming off the guide sleeve 3, and only when the amplitude of the outer cylinder 20 is large, the cut-off section 13 can also move to the vicinity of the damper sheet 2, at which time the guide rod 1 and the guide sleeve 3 are relatively stationary. That is, the two form a rigid whole, which can give the outer cylinder 20 a rigid blocking force and prevent the outer cylinder 20 from colliding with each other.
  • a ferrule 5 is disposed between the damper sheet 2 and the guide sleeve 3, and an annular first notch 33 is opened inside the open end of the guide sleeve 3,
  • the ferrule 5 is located at the first slot 33;
  • a second slot 51 is defined in the inner side of the ferrule 5, and the damper sheet 2 is located at the second slot 51 and is in contact with the radial edge of the first slot 33.
  • the damper sheet 2 is fixed by the ferrule 5 and the first notch 33, and the thickness of the ferrule 5 is equal to the thickness of the first notch 33, so that the connection fixing structure at both ends of the damper sheet 2 is ensured to be flush;
  • the thickness of 2 is greater than the thickness of the second notch 51, that is, a portion of the damper sheet 2 projects inwardly, and the working portion of the guide bar 1 moves relative to the convex portion of the damper sheet 2 to generate a frictional damping force.
  • At least two buckles 52 are arranged on the outer side of the ferrule 5, and the first slot 33 is provided with a card slot 331 matching the buckle 52, and the buckle 52 is affixed.
  • the plurality of buckles 52 are evenly disposed in the axial direction of the ferrule 5; thus, by providing the buckle 52 and the card slot 331, the fixing between the ferrule 5 and the guide sleeve 3 is enhanced. Sex, while making the assembly operation of the ferrule 5 simple.
  • a rib 53 extending radially outward is further provided at the end of the ferrule 5, and the rib 53 is located at the end of the open end of the guide sleeve 3.
  • the lateral damper device 50 in order to make the lateral damper device 50 provide the required variable damping force, it is necessary to design the lateral damper device 50 for a specific washing machine model, and derive the lateral design for the washing machine according to the known conditions of the washing machine.
  • the main parameters of the damper device 50 ensure that the lateral damper device 50 has the above-described effects.
  • the washing machine includes a casing 10, a set outer cylinder 20 and an inner cylinder 30 disposed in the casing 10.
  • the outer cylinder 20 is hoisted at the corners of the four corners of the casing 10 by four booms 40.
  • the washing machine crash box mainly occurs in the dehydration start stage, when the base frequency of the excitation force corresponding to the washing machine speed is close to the common frequency of the internal and external barrel crane boom system, the inner and outer cylinders resonate, and the amplitude of the outer cylinder 20 increases significantly. As a result, the outer cylinder 20 collides with the casing, and a collision box occurs.
  • the damping structure 50 is mainly used to provide a horizontal damping force, and a damping force is generated between the guiding rod 1 and the damping piece 2; the damping structure 50 needs to prevent the washing machine from colliding at a low speed dehydration and ensure high speed dehydration. The noise of the whole machine will not increase due to the increase of the vibration transmitted to the box.
  • the damping structure gives sufficient damping force to prevent the outer tube 20 from colliding with the box; 20 Within the safe amplitude of stable operation, the damping structure gives less or no damping force; that is, the damping structure 50 provides a variable damping force, which requires the damping rod 1 to have a hollow section 12 in the middle, And the working section 11 at the two ends of the idle section 11, when the outer cylinder 20 is within the safe amplitude of the stable operation, the idle section 11 is located at the damper sheet 2, and the guide rod 1 and the damper sheet 2 are not in contact with each other.
  • the damping force is generated, and the vibration on the outer cylinder 20 cannot be transmitted to the casing 10 through the damping structure 50, thereby avoiding an increase in noise; when the vibration amplitude of the outer cylinder 20 is large, there is a risk of hitting the barrel, and at this time, the guide rod 1 is Stretch The amplitude is relatively large, the working section 12 is positioned at the damper 2, a damping force generated at this time to prevent vibration of the outer cylinder 20, the outer cylinder 20 so that the vibration amplitude is reduced.
  • the main parameters of the damping structure 50 designed for the washing machine are derived from the known conditions of the washing machine, ensuring that the damping structure 50 has the above-described effects.
  • the design method in this embodiment includes the following steps:
  • the dehydration start eccentric mass m e of the washing machine is determined; the highest resonance frequency f PMax of the low-frequency rigid body mode of the washing machine is a value simulated under ideal conditions; the calculated eccentric force Fe The maximum eccentric force when dehydrating the washing machine.
  • the anti-collision box device 50 needs to provide the anti-collision box balance force F C , wherein F C >F e -F h -F a is required .
  • F h is the horizontal balance force provided by the boom 40
  • F a is the elastic restoring force provided by the motor shaft.
  • F h is related to the deformation amount of the spring of the boom 40 and the angle between the boom 40 and the vertical direction
  • F a is related to the deviation angle of the motor shaft. Since F h is usually small and F a is related to the main shaft yaw angle, these two forces are replaced by the safety factor s1.
  • each washing machine is guaranteed to have at least two or more anti-collision box devices 50, and each washing machine at least guarantees two anti-collision box devices placed in different directions to ensure that when the outer tube 20 vibrates in the horizontal direction,
  • the crash box device 50 dampens the vibration of the outer cylinder 20 from two directions.
  • the number of crash box devices 50 is recommended to be an integer multiple of 2, preferably 2, 4, 6, 8.
  • the angle between the adjacent two anti-collision box devices 50 on the horizontal plane is between 30° and 150°, preferably four anti-collision box devices 50 are used, and the adjacent two anti-collision box devices 50 are perpendicular to each other. That is, the angle between the adjacent two crash box devices 50 on the horizontal plane is 90°.
  • the damper sheet 2 is circular
  • ⁇ c is the inner diameter of the damper sheet 2
  • the maximum diameter ⁇ w of the working section 11 of the guide rod 1 and the inner diameter ⁇ c of the damper sheet 2 need to be selected to a value, and Calculate another.
  • the diameter ⁇ z of the idle section 12 of the guide rod 1 is determined according to the inner diameter ⁇ c of the damper sheet 2.
  • the displacement amplitude d O is a displacement amplitude in the horizontal direction
  • s 4 is a safety factor
  • s 4 > 1 to ensure that the outer cylinder 40 is In stable operation
  • the idle section 12 is located at the damper sheet 2, and the damper structure 50 does not provide a damping force; wherein, 1 ⁇ s 4 ⁇ 3, but the value of s 4 cannot be too large, and the vibration amplitude of the outer cylinder 20 of the washing machine is avoided.
  • the working section of the guide bar 1 is not at the damper sheet 2, preferably, 1 ⁇ s 4 ⁇ 1.5.
  • L Max E The minimum spacing between the guide rod length L z idling section 1, and the outer cylinder 20 and the housing 10, determine the length L w guide rod 11 of the working section.
  • the working length of the guide rod is L w ⁇ L Max - L z /2, wherein L Max is the minimum distance between the outer cylinder and the casing.
  • L Max is the minimum distance between the outer cylinder and the casing.
  • the rigidity of the outer cylinder 20 is such that the impingement of the outer cylinder 20 is avoided, and thus the length of the guide rod working section L w ⁇ L Max - L z /2 is set.
  • the maximum diameter ⁇ w of the working section 11 of the guiding rod 1 is: the maximum diameter ⁇ w of the working section 11 of the guiding rod 1 , the working section length L w , the diameter of the idle section 12 ⁇ z , and the length of the idle section 12 L z , the inner diameter ⁇ c of the damper sheet 2.
  • damping structure 50 The details of the damping structure 50 are designed according to the above main parameters, wherein the guiding rod 1 can have a variety of specific structures, which are described in detail below.
  • the idle section 12 is an equal diameter cylindrical section having a diameter of ⁇ z and a length L z , and the maximum diameter of the working section 11 of the guide rod 1 is idling.
  • the frustum-shaped transition section extends all the way to the cut-off section 13, that is, the diameter of the junction of the frustum-shaped transition section and the cut-off section 13 is the maximum diameter ⁇ w of the working section 11, and the frustum-shaped transition section is the working section 11.
  • the idle section 12 is an equal diameter cylindrical section having a diameter of ⁇ z and a length L z
  • the working section 11 has an equal diameter cylindrical section having a diameter of ⁇ w 111 and the frustum-shaped transition section 112, the diameter of any cross-section of the frustum-shaped transition section is located between the maximum diameter ⁇ w of the working section 11 of the guide rod 1 and the diameter ⁇ z of the idle section 13 .
  • the truncated cone transition section 112 is a frustum between the equal diameter cylindrical section 111 and the idle section 12, the cutoff section 13 is located at both ends of the guide rod 1, and the cutoff section 13 is also an equal diameter cylindrical section.
  • the frustum-shaped transition section 112 may also be designed as a curved transition section, and the diameter of any cross section of the arcuate transition section is located at the maximum diameter ⁇ w and the idle section of the working section 11 of the guide rod 1
  • the diameter of 13 is between ⁇ z .
  • the idle section 12 is an equal diameter cylindrical section having a diameter of ⁇ z and a length L z
  • the cutoff section 13 is an equal diameter cylindrical section
  • the working section 11 has An equal diameter cylindrical section 111 having a diameter of ⁇ w and a cylindrical transition section 113 having a diameter between the maximum diameter ⁇ w of the working section 11 and the diameter ⁇ z of the idle section 13 .
  • the design process is illustrated by taking the 8kg platform pulsator washing machine as an example.
  • the design method is as follows:
  • the damping structure 50 can be disposed between any two of the washing machine outer cylinder 20, the casing 10 and the boom 40 for providing a level.
  • the damping of the direction dampens the lateral vibration of the outer cylinder or the vibration in the horizontal direction.
  • the damper sheet 2 is fixed on the inner side of the guide sleeve 3, and the guide rod 1 is telescopically located in the guide sleeve 3.
  • the guide sleeve 3 is a cylindrical structure with one end open, and the damper sheet 2 is disposed inside the open end of the guide sleeve 3, and the guide sleeve The other end of 3 is provided with a first hinge portion 31.
  • the vibration of the outer cylinder 20 drives the guiding rod 1 to move relative to the guiding sleeve 3 to provide a variable damping force;
  • the vent hole 32 is formed in the sleeve wall at the opposite end of the opening end of the guiding sleeve 3, and the guiding rod 1 is in the guiding sleeve 3
  • gas can flow out through the vent 32 or into the guide sleeve 3, avoiding the free end of the guide rod 1 enclosing a gas in the guide sleeve 3, so that the gas in the guide sleeve 3 can be moved when the guide rod 1 moves It flows out or is replenished so that when the vibration of the outer cylinder 20 is slow, gas damping is not formed.
  • the guide rod 1 is a hollow rod having an open end, the open end of which is located in the guide sleeve 3, and the hollow rod is provided by the guide rod 1 position, and the chamber of the guide rod 1 is connected with the chamber of the guide sleeve 3. In this way, a large accommodation space is formed, and when the guide rod 1 telescopically moves in the guide sleeve 3, the influence of the airflow flowing through the through hole 32 on the guide rod 1 is reduced; and the other end of the guide rod 1 is provided with the second hinge portion. 14.
  • a ferrule 5 is disposed between the damper sheet 2 and the guide sleeve 3, and an annular first notch 33 is opened inside the open end of the guide sleeve 3, and the ferrule 5 is located at the A notch 33 is formed; a second slot 51 is defined in the inner side of the ferrule 5, and the damper sheet 2 is located at the second slot 51 and is in contact with the radial edge of the first slot 33.
  • the damper sheet 2 is fixed by the ferrule 5 and the first notch 33, and the thickness of the ferrule 5 is equal to the thickness of the first notch 33, so that the connection fixing structure at both ends of the damper sheet 2 is ensured to be flush;
  • the thickness of 2 is greater than the thickness of the second notch 51, that is, a portion of the damper sheet 2 projects inwardly, and the working portion of the guide bar 1 moves relative to the convex portion of the damper sheet 2 to generate a frictional damping force.
  • At least two buckles 52 are arranged on the outer side of the ferrule 5, and the first slot 33 is provided with a card slot 331 matching the buckle 52, and the buckle 52 is affixed.
  • the plurality of buckles 52 are evenly disposed in the axial direction of the ferrule 5; thus, by providing the buckle 52 and the card slot 331, the fixing between the ferrule 5 and the guide sleeve 3 is enhanced. Sex, while making the assembly operation of the ferrule 5 simple.
  • a rib 53 extending radially outward is further provided at the end of the ferrule 5, and the rib 53 is located at the end of the open end of the guide sleeve 3.

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Abstract

一种洗衣机阻尼结构及设计方法、横向减震装置及洗衣机，所述阻尼结构（50）包括导向套（3）、以及一端伸入所述导向套（3）内部的导向杆（1），所述导向套（3）的内侧设有与导向杆（1）配合产生阻尼力的阻尼片（2），所述导向杆（1）具有中部的空载段（12）、以及位于空载段（12）两端的工作段（11），所述空载段（12）的直径小于所述阻尼片（2）的内径，所述工作段（11）的直径大于所述阻尼片（2）的内径；通过设有空载段（12）以及工作段（11），实现提供可变的阻尼力，在外筒（20）振动较大时，阻尼结构（50）给予足够的阻尼力，避免外筒（20）撞箱；并且在洗衣机外筒（20）在稳定运行的安全振幅内，阻尼结构（50）给予较小的阻尼力或不给予阻尼力；既能防止洗衣机在低速脱水时发生撞箱问题，又保证高速脱水时不会由于传递到箱体（10）上的振动增大而导致整机噪声增大。

Description

一种洗衣机阻尼结构及设计方法、横向减震装置及洗衣机 技术领域
本发明属于洗衣机技术领域，具体涉及一种洗衣机阻尼结构及设计方法、横向减震装置及洗衣机。
背景技术
目前洗衣机减振主要通过悬挂于洗衣机四角位置的吊杆来吊挂洗衣机内外桶，在洗涤和脱水过程中，内外桶都是通过压缩吊杆降低振动，吊杆通过自身的阻尼来消耗内外筒的振动。但是吊杆的使用只能缓冲竖直方向的振动，无法降低横向振动，导致在大偏心下撞箱，影响洗衣机的容积比和启动能力。
波轮洗衣机脱水过程中，转速由零一直升高到700转甚至更高。衣物不平衡导致的偏心载荷随转速升高而逐渐增大，偏心载荷对应的激励力基频由零升高到十几赫兹。而波轮洗衣机一般在1～3Hz附近存在明显的固有模态，当洗衣机转速经过其模态频率时，会引起洗衣机出现共振现象。如果不能较好的控制洗衣机的共振现象，会导致洗衣机出现撞箱甚至损坏。
为了解决洗衣机撞箱问题，在专利CN201020229971.0中将弹簧固定在外筒与箱体之间，提供恢复力。当发生共振时外筒与箱体之间存在较大的位移，导致连接外筒与箱体之间的弹簧被拉伸或者压缩而产生恢复力，减小外筒与箱体之间的位移，防止洗衣机振动过大而产生撞箱问题。但当洗衣机转速超过其对应的模态频率而达到稳定转速而正常脱水工作时，该弹簧会将外筒上的振动传递到箱体上，导致洗衣机箱体振动发声，整机噪声升高。
发明内容
本发明针对现有技术中存在的上述问题，提供一种洗衣机阻尼结构，既能防止洗衣机在低速脱水时发生撞箱问题，又能保证高速脱水时不会由于传递到箱体上的振动增大而导致整机噪声增大。
为达到上述技术目的，本发明采用以下技术方案实现：
一种洗衣机阻尼结构，包括导向套、以及一端伸入所述导向套内部的导向杆，所述导向套的内侧设有与导向杆配合产生阻尼力的阻尼片，所述导向杆具有中部的空载段、以及位于空载段两端的工作段，所述空载段的直径小于所述阻尼片的内径，所述工作段的直径大于所述阻尼片的内径；在洗衣机稳定运行时，所述空载段位于所述阻尼片处；在洗衣机外筒振动较大时，所述工作段位于所述阻尼片处。
进一步的，在所述工作段具有圆柱形的主工作段、以及设置在所述空载段与主工作段之间的变径段，所述变径段的任一截面的直径均位于所述空载段直径和工作段直径之间。
进一步的，所述导向杆还具有沿所述工作段向端部延伸的截止段，所述导向杆相对于导向套伸缩运动，当所述导向杆的截止段运动到所述阻尼片附近时两者的相对运动停止。
进一步的，所述导向套为一端开口的筒状结构，所述阻尼片设在所述导向套的开口端的内侧，所述导向套的另一端设有第一铰接部。
进一步的，所述导向杆为具有一端开口的中空杆，其开口端位于导向套内，所述导向杆的另一端设有第二铰接部。
进一步的，所述阻尼片和导向套之间设有卡套，在所述导向套的开口端内侧开设有环形的第一槽口，所述卡套位于第一槽口处；在所述卡套的内侧开设有第二槽口，所述阻尼片位于第二槽口处、并与第一槽口的径向边接触。
进一步的，所述卡套的端部还设有沿径向向外延伸的挡沿，所述挡沿位于所述导向套开口端的端部。
进一步的，所述卡套的外侧周向排布有至少两个卡扣，所述第一槽口上开设有与所述卡扣相匹配的卡槽，所述卡扣卡合固定在所述卡槽内。
进一步的，在所述导向套开口端相对的一端的套壁上开设有通气孔。
基于上述的洗衣机阻尼结构，本发明还提供一种上述阻尼结构的设计方法，所述设计方法包括如下步骤：
A.根据所述洗衣机自身的参数，确定洗衣机脱水时的最大偏心力Fe；进而确定阻尼结构的阻尼力F D，最终确定导向杆的工作段与阻尼片之间的过盈间距d c；
B、根据过盈间距d c,在所述导向杆的工作段最大直径φ w和阻尼片内径φ c中，依据φ w＝φ c+2d c，在选定其中一个的尺寸后，另外一个的尺寸可以计算得出；
C.根据阻尼片内径φ c，确定导向杆空载段直径φ z；
D.根据洗衣机脱水稳定运行阶段外筒位移幅值d O，确定导向杆空载段的长度L z；
E.根据导向杆空载段的长度L z、以及外筒与箱体之间的最小间距L Max，确定导向杆工作段长度L w；
F.根据上述步骤中阻尼结构的主要参数，得到针对所述洗衣机设计的阻尼结构。
进一步的，在步骤A中，根据洗衣机脱水启动偏心质量m e、洗衣机内筒直径r 1、以及低频刚体模态的最高共振频率f PMax，计算出洗衣机脱水时的偏心力Fe＝m e*(2πf PMax) 2r I。
进一步的，在步骤A中还具有步骤A1，根据偏心力Fe，确定防撞箱平衡力F C＝s 1F e；其中s 1为安全系数。
优选的，0.1<s 1<3。
进一步的，在步骤A中还具有位于步骤A1之后的步骤A2，根据防撞箱平衡力F C、以及洗衣机上计划设置的阻尼结构的数量N，计算出每个阻尼结构的阻尼力为F D；阻尼力F D＝2F C/N。
进一步的，在步骤A中还具有位于步骤A2之后的步骤A3，根据阻尼结构的阻尼力为F D、以及选用的阻尼片的摩擦系数c,确定导向杆的工作段与阻尼片间的正压力F N＝F D/c。
进一步的，在步骤A中还具有位于步骤A3之后的步骤A4，根据正压力F N、以及所述阻尼片的等效刚度k c，确定所述导向杆的工作段与阻尼片之间的过盈间距d c＝F N/k c。
进一步的，在步骤C中，导向杆空载段直径φ z＝s 3φ c，其中s 3为安全系数，0.3<s 3≤1。
进一步的，在步骤D中，导向杆空载段的长度L z＝2s 4d O,其中s 4为安全系数，s 4>1。
优选的，1<s 4<3。
进一步的，在步骤E中，导向杆工作段长度L w＝s 5L Max-L z/2,其中s 5为安全系数，0.2<s 5<1。
进一步的，所述导向杆的工作段最大直径φ w与所述空载段直径φ z之间具有锥台形过渡段。
进一步的，所述导向杆的工作段最大直径φ w与所述空载段直径φ z之间具有弧面形过渡段，所述弧面形过渡段的任一横截面的直径均位于所述导向杆的工作段最大直径φ w与空载段直径φ z之间。
进一步的，所述导向杆的工作段最大直径φ w与所述空载段直径φ z之间至少具有一段圆柱形过渡段，所述圆柱形过渡段的直径位于所述导向杆的工作段最大直径φ w与空载段直径φ z之间。
基于上述的洗衣机阻尼结构，本发明还提供一种具有该阻尼结构的洗衣机，既能防止洗衣机在低速脱水时发生撞箱问题，又能保证高速脱水时不会由于传递到箱体上的振动增大而导致整机噪声增大。
一种洗衣机，包括箱体、以及位于箱体内的套装设置的外筒和内筒，所述外筒通过吊杆吊装在所述箱体上，在所述外筒、箱体、吊杆三者中的任意两者之间设有上述的阻尼结构。
本发明另一目的在于提供一种具有上述阻尼结构的洗衣机横向减震装置，包括与所述阻尼结构一端铰接的第一安装座、以及竖向设置的滑杆，所述阻尼结构的另一端可滑动的套装在所述滑杆上，所述滑杆的两端分别设有第二安装座。
进一步的，所述阻尼结构上开设有滑孔，所述滑杆穿过所述滑孔，所述滑杆与滑孔之间设有第二缓冲垫。
进一步的，所述第二缓冲垫包括第二筒形主体、沿所述第二筒状主体上下两端向外延伸的第二翻边，两个所述第二翻边与第二筒形主体形成与所述滑孔边缘相匹配的容纳槽。
进一步的，在所述滑杆上设有上下两个限位凹槽，所述滑孔在滑杆上两个限位凹槽之间滑动。
进一步的，所述第一安装座上设有销轴，所述阻尼结构上设有与所述销轴相匹配的销孔，所述销轴与销孔之间设第一缓冲垫。
进一步的，所述第一安装座具有平行设置的两个安装板，在两个所述安装板上分别相对设有相互靠近的销轴座，所述销孔位于两个销轴座之间，在所述销轴座上开设有销轴孔，所述销轴穿过所述销轴孔。
进一步的，所述阻尼结构包括导向杆、以及套装在所述导向杆外侧的导向套，所述导向套的内侧设有与导向杆配合产生阻尼力的阻尼片，所述导向杆具有中部的空载段、以及位于空载段两端的工作段，所述空载段的直径小于所述阻尼片的内径，所述工作段的直径大于所述阻尼片的内径。
进一步的，所述导向杆一端位于所述导向套内，另一端套装在滑杆上；所述导向套为一端开口的筒状结构，另一端与第一安装座铰接。
进一步的，在所述工作段具有圆柱形的主工作段、以及设置在所述空载段与主工作段之间的变径段，所述变径段的任一截面的直径均位于所述空载段直径和工作段直径之间。
进一步的，所述导向杆还具有沿所述工作段向端部延伸的截止段，所述导向杆相对于导向套伸缩运动，当所述导向杆的截止段运动到所述阻尼片处时两者的相对运动停止。
进一步的，所述阻尼片和导向套之间设有卡套，在所述导向套的开口端内侧开设有环形的第一槽口，所述卡套位于第一槽口处；在所述卡槽的内侧开设有第二槽口，所述阻尼片位于第二槽口处、并与第一槽口的径向边接触。
进一步的，所述卡套的端部还设有沿径向向外延伸的挡沿，所述挡沿位于所述导向套开口端的端部。
进一步的，所述卡套的外侧轴向排布有至少两个卡扣，所述第一槽口上开设有与所述卡扣相匹配的卡槽，所述卡扣位于所述卡槽内。
进一步的，在所述导向套开口端相对的一端的套壁上开设有通气孔。
本发明提供的阻尼结构，用于提供水平方向的阻尼力，通过设置所述导向杆具有中部的空载段、以及位于空载段两端的工作段，实现提供可变的阻尼力，在外筒振动较大时，阻尼结构给予足够的阻尼力，避免外筒撞箱；并且在洗衣机外筒在稳定运行的安全振幅内，阻尼结构给予较小的阻尼力或不给予阻尼力；这样在洗衣机稳定运行时，所述空载段位于所述阻尼片处；在洗衣机外筒振动较大时，所述工作段位于所述阻尼片处；这样既能防止洗衣机在低速脱水时发生撞箱问题，又能保证高速脱水时不会由于传递到箱体上的振动增大而导致整机噪声增大。
结合附图阅读本发明的具体实施方式后，本发明的其他特点和优点将变得更加清楚。
附图说明
图1为本发明所提出的阻尼结构的一个实施例的结构示意图；
图2为图1的剖视结构示意图；
图3为图2中阻尼片处的放大***图；
图4为图2中阻尼杆的结构示意图；
图5为设有图1中阻尼结构的洗衣机；
图6为阻尼结构的设计方法的流程图；
图7为导向杆的一种具体结构示意图；
图8为本发明所提出的洗衣机横向减震装置的一个实施例的结构示意图；
图9为图8中A区域的放大结构示意图；
图10为图8的剖视结构示意图；
图11为图10中B区域的放大结构示意图；
图12为图10中C区域的放大结构示意图；
图13为图10中D区域的放大结构示意图；
图14为导向杆的第一种具体结构示意图；
图15为导向杆的第三种具体结构示意图；
具体实施方式
为使本发明实施例的目的、技术方案和优点更加清楚，下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述。
在本发明的描述中，需要说明的是，术语“内”、“上”、“下”、“左”、“右”等指示的方位或位置关系为基于附图所示的位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。此外，术语“第一”、“第二”、“第三”仅用于描述目的，而不能理解为指示或暗示相对重要性。
实施例一
参阅图1-图7，是本发明所提出的阻尼结构的一个实施例，洗衣机包括箱体10、设置在箱体10内的套装设置的外筒20和内筒30，外筒20通过四个吊杆40吊装在箱体10四个角部的角板上；洗衣机撞箱主要发生在脱水启动阶段，当洗衣机转速对应的激励力基频与内外桶机吊杆组成***的共有频率接近时，内外筒发生共振，外筒20振幅明显增大，从而导致外筒20碰撞箱体，发生撞箱。为了防止发生撞桶，在洗衣机上设有至少两个相对设置的阻尼结构50，用于提供水平方向的阻尼力；阻尼结构50设置在箱体10、外筒20、吊杆40三者中的其中两者之间，优选的设置在箱体10和外筒20之间，由于箱体10的相对静止，可以提供更有效的阻尼力避免撞桶。
本实施例中，阻尼结构50包括导向杆1、以及套装在导向杆1外侧的导向套3，在导向套3的内侧设有与导向杆1配合产生阻尼力的阻尼片2，导向杆1具有中部的空载段12、以及位于空载段12两端的工作段11，其中空载段12的直径小于阻尼片2的内径，工作段11的直径大于阻尼片2的内径。
本实施例中，通过导向杆1和阻尼片2之间产生阻尼力，避免发生撞桶；通过导向杆1具有空载段12和工作段11，在洗衣机稳定运行时，空载段12位于阻尼片2处，也就是在洗衣机外筒20在稳定运行的安全振幅内，阻尼结构给予较小的阻尼力或不给予阻尼力，因而外筒20上的振动不能通过阻尼结构50传递到箱体10上，避免了噪音的增大；在洗衣机外筒振动较大时，具有撞桶的风险，此时导向杆1的伸缩幅度也比较大，工作段12位于阻尼片2处，此时产生阻止外筒20振动的阻尼力，使得外筒20的振动幅度减小，避免撞桶；也就是阻尼结构50提供的为变阻尼力，阻尼结构50需要既能防止洗衣机在低速脱水时发生撞箱问题，又能保证高速脱水时不会由于传递到箱体上的振动增大而导致整机噪声增大。
本实施例中，参见图4所示，空载段12为圆柱形，工作段11具有圆柱形的主工作段111以及设置在空载段12与主工作段111之间的变径段112，当然变径段112上直径大于阻尼片2的内径的部分，均与阻尼片2接触产生阻尼力；变径段112为锥台形，也就是说变径段112的母线为连接空载段12与主工作段111之间一端倾斜的直线，变径段112的任一截面的直径均位于空载段12的直径和主工作段111的直径之间。通设置变径段112使得导向杆1在伸缩运动是可以平稳的在空载段12和工作段11之间过渡，变径段112经过阻尼片2时，变径段112与阻尼片2之间的阻尼力逐渐变化。
本实施例中，导向杆1还具有沿工作段11向端部延伸的截止段13，截止段13的直径肯定大于工作段11的直径，导向杆1相对于导向套3伸缩运动，当导向杆1的截止段14运动到阻尼片2附近时两者的相对运动停止。通过设置截止段13可以避免导向杆1脱离导向套3，同时只有在外筒20的振幅较大时，截止段13也可能移动到阻尼片2附近，此时导向杆1与导向套3的相对静止，也就是两者形成一个刚性的整体，能够给予外筒20刚性的阻止力，阻止外筒20箱体的相碰。
本实施例中，参见图2所示，导向套3为一端开口的筒状结构，阻尼片2设在导向套3的开口端的内侧，导向套3的另一端设有第一铰接部31。外筒20的振动，带动导向杆1相对于导向套3移动，提供变阻尼力；在导向套3开口端相对的一端的套壁上开设有通气孔32，在导向杆1在导向套3内伸缩时移动时，气体可以经通气孔32流出或进入导向套3内，避免导向杆1的自由端将一段气体封闭在导向套3内，这样在导向杆1移动时导向套3内的气体可以流出或得到补充，这样在外筒20的振动缓慢时，不会形成气体阻尼。
本实施例中，导向杆1为具有一端开口的中空杆，其开口端位于导向套3内，通过设置导向杆1位 空心杆，并使得导向杆1的腔室与导向套3的腔室相连通，这样形成较大的容纳空间，在导向杆1在导向套3内伸缩移动时，减少了流经通孔32的气流对导向杆1的影响；导向杆1的另一端设有第二铰接部14。
参见图3所述，为了阻尼片2的固定，在阻尼片2和导向套3之间设有卡套5，在导向套3的开口端内侧开设有环形的第一槽口33，卡套5位于第一槽口33处；在卡套5的内侧开设有第二槽口51，阻尼片2位于第二槽口51处、并与第一槽口33的径向边接触。这样阻尼片2被卡套5和第一槽口33限位固定，卡套5的厚度与第一槽口33的厚度相等，这样保证了位于阻尼片2两端的连接固定结构平齐；阻尼片2的厚度大于第二槽口51的厚度，也就是阻尼片2有一部分向内凸出，导向杆1的工作段与阻尼片2的凸出部分相对移动产生摩擦阻尼力。
为了卡套5的固定牢固，在卡套5的外侧周向排布有至少两个卡扣52，第一槽口33上开设有与卡扣52相匹配的卡槽331，并且卡扣52卡合固定在卡槽331内，在卡套5的轴向均布有四个卡扣52；这样通过设置卡扣52和卡槽331，有利于增加卡套5与导向套3之间固定的牢固性，同时使得卡套5的装配操作简单。
为了进一步增加卡套5固定后的稳定性和美观性，在卡套5的端部还设有沿径向向外延伸的挡沿53，挡沿53位于导向套3开口端的端部。这样通过设置挡沿53增加了卡套5的受力性能，提高卡套5的稳定性，以及有利于增加卡套5和导向套3装配后的美观性。
本实施例中，为了使得阻尼结构50可以提供所需的变阻尼力，需要针对具体的洗衣机型号进行阻尼结构50的设计，根据洗衣机的已知条件推导出针对该洗衣机设计的阻尼结构50的主要参数，保证阻尼结构50具有上述的效果。
参见图6所示，为本实施例中阻尼结构50的设计方法，包括如下步骤：
A.根据洗衣机自身的参数，确定洗衣机脱水时的最大偏心力Fe；进而确定阻尼结构的阻尼力F D，最终确定导向杆的工作段与阻尼片之间的过盈间距d c。
具体的，根据洗衣机脱水启动偏心质量m e、洗衣机内筒直径r 1、以及低频刚体模态的最高共振频率f PMax，计算出洗衣机脱水时的偏心力Fe＝m e*(2πf PMax) 2r I。其中根据该型号洗衣机设计时确定的抗偏心能力，确定洗衣机脱水启动偏心质量m e；洗衣机低频刚体模态的最高共振频率f PMax是在理想条件下模拟得到的数值；计算得出的偏心力Fe为洗衣机脱水时的最大偏心力。
步骤A1.根据洗衣机脱水时的偏心力Fe，确定防撞箱平衡力F C＝s 1F e；其中s 1为安全系数，优选的，0.1<s 1<3。
具体的，为了克服洗衣机脱水时的偏心力，避免洗衣机外筒20撞箱，防撞箱装置50需要提供防撞箱平衡力F C，其中需满足F C>F e-F h-F a，其中F h为吊杆40提供的水平方向的平衡力,F a为电机主轴提供的弹性恢复力。F h与吊杆40弹簧的变形量及吊杆40与竖直方向的夹角相关，F a与电机主轴偏角有关。 由于通常情况下F h较小及F a与主轴偏角有关，因此通过安全系数s1来代替这两个力。
步骤A2.根据防撞箱平衡力F C、以及洗衣机上计划设置的阻尼结构50的数量N，计算出每个阻尼结构50的阻尼力为F D；阻尼力F D＝2F C/N。
具体的，每台洗衣机至少保证有两个及以上的防撞箱装置50，且每台洗衣机至少保证有两个不同方向放置的防撞箱装置，以保证在外筒20在水平方向振动时，两个防撞箱装置50从两个方向阻尼外筒20的振动。防撞箱装置50的数量推荐为2的整数倍，优选2、4、6、8。相邻的两个防撞箱装置50在水平面上的夹角在30°至150°间，优选的采用四个防撞箱装置50，且相邻的两个防撞箱装置50相互垂直，也就是相邻的两个防撞箱装置50在水平面上的夹角为90°。
步骤A3.根据阻尼结构50的阻尼力为F D、以及选用的阻尼片2的摩擦系数c,确定导向杆1的工作段11与阻尼片2之间的正压力F N＝F D/c。其中，F N与阻尼片2与导向杆1的接触面积及接触正应力成正比。
步骤A4.根据正压力F N、以及阻尼片2的等效刚度k c，确定导向杆1的工作段11与阻尼片2之间的过盈间距d c＝F N/k c。
B.根据过盈间距d c,在导向杆1的工作段11最大直径φ w和阻尼片2的内径φ c中，依据φ w＝φ c+2d c，在选定其中一个的尺寸后，另外一个的尺寸可以计算得出。
具体的，阻尼片2为圆环形，φ c为阻尼片2的内圆直径，导向杆1的工作段11最大直径φ w和阻尼片2的内径φ c需要向选定一个的数值，并计算得到另一个。
C.根据阻尼片2的内径φ c，确定导向杆1的空载段12直径φ z。
具体的，导向杆1的空载段11的直径φ z肯定要小于阻尼片2的内径φ c，以保证空载段12与阻尼片2之间没有阻尼力；优选的φ z＝s 3φ c，其中s 3为安全系数，0.3<s 3≤1。
D.根据洗衣机脱水稳定运行阶段外筒20的位移幅值d O，确定导向杆1的空载段12的长度L z。
具体的，位移幅值d O为水平方向的位移幅度，导向杆1的空载段12的长度L z＝2s 4d O,其中s 4为安全系数，s 4>1以保证外筒40在稳定运行时，空载段12位于阻尼片2处，阻尼结构50不提供阻尼力；其中，1<s 4<3，但s 4的取值也不能过大，避免洗衣机外筒20振动幅度较大时，导向杆1的工作段没有处于阻尼片2处，优选的，1<s 4<1.5。
E.根据导向杆1的空载段的长度L z、以及外筒20与箱体10之间的最小间距L Max，确定导向杆1的工作段11的长度L w。
具体的，为了保证外筒不发生撞箱，导向杆工作段长度L w<L Max-L z/2，其中L Max为外筒与箱体之间的最小间距。在导向杆1上还具有沿工作段11向端部延伸的截止段13，当导向杆1的截止段13运动到阻尼片2附近时两者的相对运动停止，也就是此时阻尼结构50给予外筒20刚性的阻力，避免外筒20的撞桶，因而设置导向杆工作段长度L w<L Max-L z/2。为了进一步保证安全性，优选L w＝s 5L Max-L z/2,s 5为安全系数，优选0.2<s 5<1。
F.根据上述步骤中阻尼结构50的主要参数，得到针对该洗衣机设计的阻尼结构。
具体的，在上述步骤中得到的阻尼结构50的几个主要参数：导向杆1的工作段11最大直径φ w、 工作段长度L w、空载段12直径φ z、空载段12的长度L z、阻尼片2的内径φ c。
参见7图所示，是导向杆1的一种具体结构形式，空载段12为直径为φ z、长度L z的等直径圆柱段，工作段11具有直径为φ w的等直径圆柱段111和锥台形过渡段112，锥台形过渡段任一横截面的直径均位于导向杆1的工作段11最大直径φ w与空载段13的直径φ z之间。锥台形过渡段112为从等直径圆柱段111与空载段12之间的锥台，截止段13位于导向杆1的两端部，截止段13也为等直径圆柱段。
为了更进一步的说明阻尼结构的设计方法，以8kg平台波轮洗衣机为例说明设计过程，设计方法如下：
A.根据洗衣机自身的参数，确定洗衣机脱水时的最大偏心力Fe；进而确定阻尼结构的阻尼力F D，最终确定导向杆的工作段与阻尼片之间的过盈间距d c。
具体的，根据洗衣机脱水启动偏心质量m e＝1kg、洗衣机内筒直径r 1＝0.25m、以及低频刚体模态的最高共振频率f PMax＝3.5Hz，计算出洗衣机脱水时的偏心力Fe＝m e*(2πf PMax) 2r I＝121N。
步骤A1.根据洗衣机脱水时的偏心力Fe，计算出防撞箱平衡力F C＝s 1F e；其中s 1为安全系数，优选s 1＝0.2，因而F C＝24N。
步骤A2.根据防撞箱平衡力F C、以及洗衣机上计划设置的阻尼结构50的数量N，计算出每个阻尼结构50的阻尼力为F D；阻尼力F D＝2F C/N。在洗衣机上采用四个阻尼结构50，即N＝4，则阻尼力F D＝24N。
步骤A3.根据阻尼结构50的阻尼力为F D、以及选用的阻尼片2的摩擦系数c＝0.3,计算出导向杆1的工作段11与阻尼片2之间的正压力F N＝F D/c＝40N。
步骤A4.根据正压力F N、以及阻尼片2的等效刚度k c，其中k c＝5×10 4N/m，计算出导向杆1的工作段11与阻尼片2之间的过盈间距d c＝F N/k cc＝0.8×10 -3m。
B.根据过盈间距d c,选取阻尼片2的内径φ c＝1.5×10 -2m，并依据φ w＝φ c+2d c，计算得出导向杆1的工作段11最大直径φ w＝1.66×10 -2m。
C.根据阻尼片2的内径φ c，其中φ z＝s 3φ c，s 3＝0.9，计算出导向杆1的空载段12直径φ z＝1.35×10 -2m。
D.根据洗衣机脱水稳定运行阶段外筒20的位移幅值d O，其中d O＝3×10 -3m，s 4＝1.2，计算出导向杆1的空载段12的长度L z＝7.2×10 -3m。
E.根据导向杆1的空载段12的长度L z、以及外筒20与箱体10之间的最小间距L Max，确定导向杆1的工作段11的长度L w＝s 5L Max-L z/2,其中L Max＝1.8×10 -2m，s 5＝0.9，则工作段11的长度L w＝9×10 -3m。
F.根据上述步骤中阻尼结构50的主要参数，得到针对该洗衣机设计的阻尼结构。
实施例二
参阅图3-图5及8-图13所示，是本发明所提出的洗衣机横向减震装置的一个实施例，洗衣机包括箱体10、设置在箱体10内的套装设置的外筒20和内筒30，外筒20通过四个吊杆40吊装在箱体10四个角部的角板上；洗衣机撞箱主要发生在脱水启动阶段，当洗衣机转速对应的激励力基频与内外桶机吊杆组成***的共有频率接近时，内外筒发生共振，外筒20振幅明显增大，从而导致外筒20碰撞箱体， 发生撞箱。为了防止发生撞桶，在洗衣机上设有至少两个相对设置的横向减震装置50，用于提供水平方向的阻尼力；横向减震装置50设置在箱体10、外筒20、吊杆40三者中的其中两者之间，优选的设置在箱体10和外筒20之间，由于箱体10的相对静止，可以提供更有效的阻尼力避免撞桶。
本实施例中，参见图8、图13和图3所示，洗衣机横向减震装置50包括阻尼结构，阻尼结构包括导向杆1、以及套装在导向杆1外侧的导向套3，在导向套3的内侧设有与导向杆1配合产生阻尼力的阻尼片2。在阻尼结构的一端铰接有第一安装座6，阻尼结构的另一端可滑动的套装在滑杆7上，滑杆7为竖向设置，并在滑杆7的两端分别设有第二安装座8。通过阻尼结构的一端可以在滑杆7上滑动，这样可以使得在外筒20在上下方向上具有振动时，阻尼结构可以通过在滑杆7上的滑动，处于水平或近似水平状态，使得阻尼结构主要用于阻尼水平方向的力，有利于增加横向阻尼的效果，避免外筒振幅过大引起的撞击箱体。
本实施例中，参见图5所示，第一安装座6固定在外筒20上，两个第二安装座8上下上下固定在箱体10上；在外筒20振动时，第一安装座6以及阻尼结构的一端一起跟随外筒20振动，当然外筒20上任一点的振动均可以分解为上下方向、左右方向、以及前后方向的振动，其中左右方向以及前后方向的振动为水平方向的振动，在安装座6跟随外筒20在上下方向具有位移时，阻尼结构的两端在上下方向上具有一定的距离，此时阻尼结构的另一端在滑杆7上的滑动、并向趋于阻尼结构水平的方向移动。由于箱体10处于相对静止状态，将第二安装座8固定在箱体10上，这样保证了滑杆7处于竖向状态，有利于保证阻尼结构的另一端在滑杆7上的滑动的流畅性，以及有利于阻尼结构的水平调整。
本实施例中，参见图10和图12所示，导向杆1一端位于导向套3内，导向杆1的另一端设有滑孔14、并套装在滑杆7上。滑杆7穿过滑孔14，并在滑杆7与滑孔14之间设有第二缓冲垫9。这样通过设置滑孔14为竖向设置、并套装在滑杆7上，可以实现导向套3的末端在滑杆7上上下滑动；通过设置第二缓冲垫9，避免了滑杆7与滑孔14之间的刚性接触，避免在滑动过程中以及阻尼结构受力时滑杆7与滑孔14之间产生噪音；并且，在阻尼结构不处于水平面内时，也就是阻尼结构的两端在上下方向具有一定的距离，此时滑孔14的轴线与滑杆7的轴线部重合，此时第二缓冲垫9的部分受到挤压发生弹性变形，同时在阻尼结构产生上下方向的拉力，使得滑孔14可以流畅的移动。
本实施例中，参见图12所示，第二缓冲垫9包括第二筒形主体91、沿第二筒状主体91上下两端向外延伸的第二翻边92，并且两个第二翻边92与第二筒形主体91形成与滑孔14边缘相匹配的容纳槽；设有在滑孔14在滑杆7上移动时，由于上下两个翻边92的挡止，使得第二缓冲垫8卡合在滑孔14的边缘，一起移动。
本实施例中，在滑杆7上设有上下两个限位凹槽71，滑孔14在滑杆7上的两个限位凹槽71之间滑动。通过设置限位凹槽71，限定了滑孔14在滑杆7上的移动范围，保证滑孔14在滑杆7上的滑动流畅性，避免出现卡死情况。
本实施例中，参见图10和图11所示，导向套3为一端开口的筒状结构，阻尼片2设在导向套3的开口端的内侧，导向套3的另一端设有销孔31、并与第一安装座6铰接。在第一安装座6上设有销轴61，销轴61竖向设置，导向杆1可以绕销轴61旋转，在销轴61与销孔31之间设第一缓冲垫，第一缓冲垫采用与第二缓冲垫9相同的结构。
具体的，第一安装座6具有平行设置的两个安装板63，在两个安装板63上分别相对设有相互靠近的销轴座62，销孔31位于两个销轴座62之间，在销轴座62上开设有销轴孔64，销轴61穿过销轴孔64。通过设置销轴座62，有利于增加销轴61装配处的结构强度，以及有利于销孔31放置到两个销轴座62之间，提高装配的速度。
本实施例中，外筒20振动时，带动导向杆1相对于导向套3移动，提供变阻尼力；在导向套3开口端相对的一端的套壁上开设有通气孔32，在导向杆1在导向套3内伸缩时移动时，气体可以经通气孔32流出或进入导向套3内，避免导向杆1的自由端将一段气体封闭在导向套3内，这样在导向杆1移动时导向套3内的气体可以流出或得到补充，这样在外筒20的振动缓慢时，不会形成气体阻尼。
本实施例中，参见图4所示，导向杆1具有中部的空载段12、以及位于空载段12两端的工作段11，其中空载段12的直径小于阻尼片2的内径，工作段11的直径大于阻尼片2的内径。通过导向杆1和阻尼片2之间产生阻尼力，避免发生撞桶；通过导向杆1具有空载段12和工作段11，在洗衣机稳定运行时，空载段12位于阻尼片2处，也就是在洗衣机外筒20在稳定运行的安全振幅内，横向减震装置给予较小的阻尼力或不给予阻尼力，因而外筒20上的振动不能通过横向减震装置50传递到箱体10上，避免了噪音的增大；在洗衣机外筒振动较大时，具有撞桶的风险，此时导向杆1的伸缩幅度也比较大，工作段12位于阻尼片2处，此时产生阻止外筒20振动的阻尼力，使得外筒20的振动幅度减小，避免撞桶；也就是横向减震装置50提供的为变阻尼力，横向减震装置50需要既能防止洗衣机在低速脱水时发生撞箱问题，又能保证高速脱水时不会由于传递到箱体上的振动增大而导致整机噪声增大。
参见图4所示，空载段12为圆柱形，工作段11具有圆柱形的主工作段111以及设置在空载段12与主工作段111之间的变径段112，当然变径段112上直径大于阻尼片2的内径的部分，均与阻尼片2接触产生阻尼力；变径段112为锥台形，也就是说变径段112的母线为连接空载段12与主工作段111之间一端倾斜的直线，变径段112的任一截面的直径均位于空载段12的直径和主工作段111的直径之间。通设置变径段112使得导向杆1在伸缩运动是可以平稳的在空载段12和工作段11之间过渡，变径段112经过阻尼片2时，变径段112与阻尼片2之间的阻尼力逐渐变化。
本实施例中，导向杆1还具有沿工作段11向端部延伸的截止段13，截止段13的直径肯定大于工作段11的直径，导向杆1相对于导向套3伸缩运动，当导向杆1的截止段14运动到阻尼片2附近时两者的相对运动停止。通过设置截止段13可以避免导向杆1脱离导向套3，同时只有在外筒20的振幅较大时，截止段13也可能移动到阻尼片2附近，此时导向杆1与导向套3的相对静止，也就是两者形成一个刚性的整体，能够给予外筒20刚性的阻止力，阻止外筒20箱体的相碰。
参见图13和图3所示，为了阻尼片2的固定，在阻尼片2和导向套3之间设有卡套5，在导向套3的开口端内侧开设有环形的第一槽口33，卡套5位于第一槽口33处；在卡套5的内侧开设有第二槽口51，阻尼片2位于第二槽口51处、并与第一槽口33的径向边接触。这样阻尼片2被卡套5和第一槽口33限位固定，卡套5的厚度与第一槽口33的厚度相等，这样保证了位于阻尼片2两端的连接固定结构平齐；阻尼片2的厚度大于第二槽口51的厚度，也就是阻尼片2有一部分向内凸出，导向杆1的工作段与阻尼片2的凸出部分相对移动产生摩擦阻尼力。
为了卡套5的固定牢固，在卡套5的外侧周向排布有至少两个卡扣52，第一槽口33上开设有与卡 扣52相匹配的卡槽331，并且卡扣52卡合固定在卡槽331内，在卡套5的轴向均布有四个卡扣52；这样通过设置卡扣52和卡槽331，有利于增加卡套5与导向套3之间固定的牢固性，同时使得卡套5的装配操作简单。
为了进一步增加卡套5固定后的稳定性和美观性，在卡套5的端部还设有沿径向向外延伸的挡沿53，挡沿53位于导向套3开口端的端部。这样通过设置挡沿53增加了卡套5的受力性能，提高卡套5的稳定性，以及有利于增加卡套5和导向套3装配后的美观性。
本实施例中，为了使得横向减震装置50可以提供所需的变阻尼力，需要针对具体的洗衣机型号进行横向减震装置50的设计，根据洗衣机的已知条件推导出针对该洗衣机设计的横向减震装置50的主要参数，保证横向减震装置50具有上述的效果。
实施例三
参见图1、2、3、5、6、7、14、15所示，是本发明所提出的洗衣机阻尼结构的设计方法的一个实施例，由于洗衣机型号的不同，发生外筒撞桶时外筒的偏心力不同，因而阻尼结构的设计是针对具体的某型号洗衣机。参见图5所示，洗衣机包括箱体10、设置在箱体10内的套装设置的外筒20和内筒30，外筒20通过四个吊杆40吊装在箱体10四个角部的角板上；由于洗衣机撞箱主要发生在脱水启动阶段，当洗衣机转速对应的激励力基频与内外桶机吊杆组成***的共有频率接近时，内外筒发生共振，外筒20振幅明显增大，从而导致外筒20碰撞箱体，发生撞箱。
阻尼结构50主要用于提供水平方向的阻尼力，通过导向杆1和阻尼片2之间产生阻尼力；阻尼结构50需要既能防止洗衣机在低速脱水时发生撞箱问题，又能保证高速脱水时不会由于传递到箱体上的振动增大而导致整机噪声增大，这就需要在外筒振动较大时，阻尼结构给予足够的阻尼力，避免外筒20撞箱；同时在洗衣机外筒20在稳定运行的安全振幅内，阻尼结构给予较小的阻尼力或不给予阻尼力；也就是阻尼结构50提供的为变阻尼力，这就需要设置阻尼杆1具有中部的空载段12、以及位于空载段11两端的工作段11，外筒20在稳定运行的安全振幅内时，空载段11位于阻尼片2处，此时导向杆1和阻尼片2之间不接触、也不产生阻尼力，外筒20上的振动不能通过阻尼结构50传递到箱体10上，避免了噪音的增大；外筒20的振动幅度多大时，具有撞桶的风险，此时导向杆1的伸缩幅度也比较大，工作段12位于阻尼片2处，此时产生阻止外筒20振动的阻尼力，使得外筒20的振动幅度减小。根据洗衣机的已知条件推导出针对该洗衣机设计的阻尼结构50的主要参数，保证阻尼结构50具有上述的效果。
参见图5、图6、图7、图14、图15所示，本实施例中的设计方法包括如下步骤：
A.根据洗衣机自身的参数，确定洗衣机脱水时的最大偏心力Fe；进而确定阻尼结构的阻尼力F D，最终确定导向杆的工作段与阻尼片之间的过盈间距d c。
具体的，根据洗衣机脱水启动偏心质量m e、洗衣机内筒直径r 1、以及低频刚体模态的最高共振频率f PMax，计算出洗衣机脱水时的偏心力Fe＝m e*(2πf PMax) 2r I。其中根据该型号洗衣机设计时确定的抗偏心能力，确定洗衣机脱水启动偏心质量m e；洗衣机低频刚体模态的最高共振频率f PMax是在理想条件下模拟得到的数值；计算得出的偏心力Fe为洗衣机脱水时的最大偏心力。
步骤A1.根据洗衣机脱水时的偏心力Fe，确定防撞箱平衡力F C＝s 1F e；其中s 1为安全系数，优选 的，0.1<s 1<3。
具体的，为了克服洗衣机脱水时的偏心力，避免洗衣机外筒20撞箱，防撞箱装置50需要提供防撞箱平衡力F C，其中需满足F C>F e-F h-F a，其中F h为吊杆40提供的水平方向的平衡力,F a为电机主轴提供的弹性恢复力。F h与吊杆40弹簧的变形量及吊杆40与竖直方向的夹角相关，F a与电机主轴偏角有关。由于通常情况下F h较小及F a与主轴偏角有关，因此通过安全系数s1来代替这两个力。
步骤A2.根据防撞箱平衡力F C、以及洗衣机上计划设置的阻尼结构50的数量N，计算出每个阻尼结构50的阻尼力为F D；阻尼力F D＝2F C/N。
具体的，每台洗衣机至少保证有两个及以上的防撞箱装置50，且每台洗衣机至少保证有两个不同方向放置的防撞箱装置，以保证在外筒20在水平方向振动时，两个防撞箱装置50从两个方向阻尼外筒20的振动。防撞箱装置50的数量推荐为2的整数倍，优选2、4、6、8。相邻的两个防撞箱装置50在水平面上的夹角在30°至150°间，优选的采用四个防撞箱装置50，且相邻的两个防撞箱装置50相互垂直，也就是相邻的两个防撞箱装置50在水平面上的夹角为90°。
步骤A3.根据阻尼结构50的阻尼力为F D、以及选用的阻尼片2的摩擦系数c,确定导向杆1的工作段11与阻尼片2之间的正压力F N＝F D/c。其中，F N与阻尼片2与导向杆1的接触面积及接触正应力成正比。
步骤A4.根据正压力F N、以及阻尼片2的等效刚度k c，确定导向杆1的工作段11与阻尼片2之间的过盈间距d c＝F N/k c。
B.根据过盈间距d c,在导向杆1的工作段11最大直径φ w和阻尼片2的内径φ c中，依据φ w＝φ c+2d c，在选定其中一个的尺寸后，另外一个的尺寸可以计算得出。
具体的，阻尼片2为圆环形，φ c为阻尼片2的内圆直径，导向杆1的工作段11最大直径φ w和阻尼片2的内径φ c需要向选定一个的数值，并计算得到另一个。
C.根据阻尼片2的内径φ c，确定导向杆1的空载段12直径φ z。
具体的，导向杆1的空载段11的直径φ z肯定要小于阻尼片2的内径φ c，以保证空载段12与阻尼片2之间没有阻尼力；优选的φ z＝s 3φ c，其中s 3为安全系数，0.3<s 3≤1。
D.根据洗衣机脱水稳定运行阶段外筒20的位移幅值d O，确定导向杆1的空载段12的长度L z。
具体的，位移幅值d O为水平方向的位移幅度，导向杆1的空载段12的长度L z＝2s 4d O,其中s 4为安全系数，s 4>1以保证外筒40在稳定运行时，空载段12位于阻尼片2处，阻尼结构50不提供阻尼力；其中，1<s 4<3，但s 4的取值也不能过大，避免洗衣机外筒20振动幅度较大时，导向杆1的工作段没有处于阻尼片2处，优选的，1<s 4<1.5。
E.根据导向杆1的空载段的长度L z、以及外筒20与箱体10之间的最小间距L Max，确定导向杆1的工作段11的长度L w。
具体的，为了保证外筒不发生撞箱，导向杆工作段长度L w<L Max-L z/2，其中L Max为外筒与箱体之间的最小间距。在导向杆1上还具有沿工作段11向端部延伸的截止段13，当导向杆1的截止段13运动到阻尼片2附近时两者的相对运动停止，也就是此时阻尼结构50给予外筒20刚性的阻力，避免外筒20的撞桶，因而设置导向杆工作段长度L w<L Max-L z/2。为了进一步保证安全性，优选L w＝s 5L Max-L z/2,s 5为安全系数，优选0.2<s 5<1。
F.根据上述步骤中阻尼结构50的主要参数，得到针对该洗衣机设计的阻尼结构。
具体的，在上述步骤中得到的阻尼结构50的几个主要参数：导向杆1的工作段11最大直径φ w、工作段长度L w、空载段12直径φ z、空载段12的长度L z、阻尼片2的内径φ c。
根据上述主要参数在对阻尼结构50进行细节的设计，其中导向杆1可以具有多种具体的结构，下面具体介绍。
参见14图所示，是导向杆1的第一种具体结构形式，空载段12为直径为φ z、长度L z的等直径圆柱段，导向杆1的工作段11最大直径处与空载段之间具有锥台形过渡段，其中锥台形过渡段的任一横截面的直径均位于导向杆1的工作段11最大直径φ w与空载段13的直径φ z之间。锥台形过渡段一直延伸到截止段13处，也就是锥台形过渡段与截止段13连接处的直径为工作段11最大直径φ w，锥台形过渡段即为工作段11。
参见7图所示，是导向杆1的第二种具体结构形式，空载段12为直径为φ z、长度L z的等直径圆柱段，工作段11具有直径为φ w的等直径圆柱段111和锥台形过渡段112，锥台形过渡段任一横截面的直径均位于导向杆1的工作段11最大直径φ w与空载段13的直径φ z之间。锥台形过渡段112为从等直径圆柱段111与空载段12之间的锥台，截止段13位于导向杆1的两端部，截止段13也为等直径圆柱段。
其他实施例中，也可以将锥台形过渡段112设计为弧面形过渡段，弧面形过渡段的任一横截面的直径均位于导向杆1的工作段11最大直径φ w与空载段13的直径φ z之间。
参见15图所示，是导向杆1的第三种具体结构形式，空载段12为直径为φ z、长度L z的等直径圆柱段，截止段13为等直径圆柱段，工作段11具有直径为φ w的等直径圆柱段111和圆柱形过渡段113，圆柱形过渡段113的直径位于工作段11的最大直径φ w与空载段13的直径φ z之间。
为了更进一步的说明阻尼结构的设计方法，以8kg平台波轮洗衣机为例说明设计过程，设计方法如下：
A.根据洗衣机自身的参数，确定洗衣机脱水时的最大偏心力Fe；进而确定阻尼结构的阻尼力F D，最终确定导向杆的工作段与阻尼片之间的过盈间距d c。
具体的，根据洗衣机脱水启动偏心质量m e＝1kg、洗衣机内筒直径r 1＝0.25m、以及低频刚体模态的最高共振频率f PMax＝3.5Hz，计算出洗衣机脱水时的偏心力Fe＝m e*(2πf PMax) 2r I＝121N。
步骤A1.根据洗衣机脱水时的偏心力Fe，计算出防撞箱平衡力F C＝s 1F e；其中s 1为安全系数，优选s 1＝0.2，因而F C＝24N。
步骤A2.根据防撞箱平衡力F C、以及洗衣机上计划设置的阻尼结构50的数量N，计算出每个阻尼结构50的阻尼力为F D；阻尼力F D＝2F C/N。在洗衣机上采用四个阻尼结构50，即N＝4，则阻尼力F D＝24N。
步骤A3.根据阻尼结构50的阻尼力为F D、以及选用的阻尼片2的摩擦系数c＝0.3,计算出导向杆1的工作段11与阻尼片2之间的正压力F N＝F D/c＝40N。
步骤A4.根据正压力F N、以及阻尼片2的等效刚度k c，其中k c＝5×10 4N/m，计算出导向杆1的工作段11与阻尼片2之间的过盈间距d c＝F N/k cc＝0.8×10 -3m。
B.根据过盈间距d c,选取阻尼片2的内径φ c＝1.5×10 -2m，依据φ w＝φ c+2d c，计算得出导向杆1的工作段11最大直径φ w＝1.66×10 -2m。
C.根据阻尼片2的内径φ c，其中φ z＝s 3φ c，s 3＝0.9，计算出导向杆1的空载段12直径φ z＝1.35×10 -2m。
D.根据洗衣机脱水稳定运行阶段外筒20的位移幅值d O，其中d O＝3×10 -3m，s 4＝1.2，计算出导向杆1的空载段12的长度L z＝7.2×10 -3m。
E.根据导向杆1的空载段12的长度L z、以及外筒20与箱体10之间的最小间距L Max，确定导向杆1的工作段11的长度L w＝s 5L Max-L z/2,其中L Max＝1.8×10 -2m，s 5＝0.9，则工作段11的长度L w＝9×10 -3m。
F.根据上述步骤中阻尼结构50的主要参数，得到针对该洗衣机设计的阻尼结构。
参见1图-图3所示，是阻尼结构50的一个具体结构，阻尼结构50可设在洗衣机外筒20、箱体10、吊杆40三者中的任意两者之间，用于提供水平方向的阻尼，阻尼外筒的横向振动或者说是水平方向的振动。阻尼片2固定在导向套3的内侧，导向杆1可伸缩的位于导向套3内，其中导向套3为一端开口的筒状结构，阻尼片2设在导向套3的开口端的内侧，导向套3的另一端设有第一铰接部31。外筒20的振动，带动导向杆1相对于导向套3移动，提供变阻尼力；在导向套3开口端相对的一端的套壁上开设有通气孔32，在导向杆1在导向套3内伸缩时移动时，气体可以经通气孔32流出或进入导向套3内，避免导向杆1的自由端将一段气体封闭在导向套3内，这样在导向杆1移动时导向套3内的气体可以流出或得到补充，这样在外筒20的振动缓慢时，不会形成气体阻尼。
参见图2，导向杆1为具有一端开口的中空杆，其开口端位于导向套3内，通过设置导向杆1位空心杆，并使得导向杆1的腔室与导向套3的腔室相连通，这样形成较大的容纳空间，在导向杆1在导向套3内伸缩移动时，减少了流经通孔32的气流对导向杆1的影响；导向杆1的另一端设有第二铰接部14。
参见图3，为了阻尼片2的固定，在阻尼片2和导向套3之间设有卡套5，在导向套3的开口端内侧开设有环形的第一槽口33，卡套5位于第一槽口33处；在卡套5的内侧开设有第二槽口51，阻尼片2位于第二槽口51处、并与第一槽口33的径向边接触。这样阻尼片2被卡套5和第一槽口33限位固定，卡套5的厚度与第一槽口33的厚度相等，这样保证了位于阻尼片2两端的连接固定结构平齐；阻尼片2的厚度大于第二槽口51的厚度，也就是阻尼片2有一部分向内凸出，导向杆1的工作段与阻尼片2的凸出部分相对移动产生摩擦阻尼力。
为了卡套5的固定牢固，在卡套5的外侧周向排布有至少两个卡扣52，第一槽口33上开设有与卡扣52相匹配的卡槽331，并且卡扣52卡合固定在卡槽331内，在卡套5的轴向均布有四个卡扣52；这样通过设置卡扣52和卡槽331，有利于增加卡套5与导向套3之间固定的牢固性，同时使得卡套5的装配操作简单。
为了进一步增加卡套5固定后的稳定性和美观性，在卡套5的端部还设有沿径向向外延伸的挡沿53，挡沿53位于导向套3开口端的端部。这样通过设置挡沿53增加了卡套5的受力性能，提高卡套5的稳定性，以及有利于增加卡套5和导向套3装配后的美观性。
以上所述，仅是本发明的较佳实施例而已，并非是对本发明作其它形式的限制，任何熟悉本专业的技术人员可能利用上述揭示的技术内容加以变更或改型为等同变化的等效实施例。但是凡是未脱离本发明技术方案内容，依据本发明的技术实质对以上实施例所作的任何简单修改、等同变化与改型，仍属于本发明技术方案的保护范围。

Claims (31)

  1. 一种洗衣机阻尼结构，包括导向套、以及一端伸入所述导向套内部的导向杆，所述导向套的内侧设有与导向杆配合产生阻尼力的阻尼片，其特征在于，所述导向杆具有中部的空载段、以及位于空载段两端的工作段，所述空载段的直径小于所述阻尼片的内径，所述工作段的直径大于所述阻尼片的内径；在洗衣机稳定运行时，所述空载段位于所述阻尼片处；在洗衣机外筒振动较大时，所述工作段位于所述阻尼片处。
  2. 根据权利要求1所述的阻尼结构，其特征在于，在所述工作段具有圆柱形的主工作段、以及设置在所述空载段与主工作段之间的变径段，所述变径段的任一截面的直径均位于所述空载段直径和工作段直径之间。
  3. 根据权利要求1所述的阻尼结构，其特征在于，所述导向杆还具有沿所述工作段向端部延伸的截止段，所述导向杆相对于导向套伸缩运动，当所述导向杆的截止段运动到所述阻尼片附近时两者的相对运动停止。
  4. 根据权利要求1所述的阻尼结构，其特征在于，所述导向套为一端开口的筒状结构，所述阻尼片设在所述导向套的开口端的内侧，所述导向套的另一端设有第一铰接部。
  5. 根据权利要求1所述的阻尼结构，其特征在于，所述导向杆为具有一端开口的中空杆，其开口端位于导向套内，所述导向杆的另一端设有第二铰接部。
  6. 根据权利要求1至5任一项所述的阻尼结构，其特征在于，所述阻尼片和导向套之间设有卡套，在所述导向套的开口端内侧开设有环形的第一槽口，所述卡套位于第一槽口处；在所述卡套的内侧开设有第二槽口，所述阻尼片位于第二槽口处、并与第一槽口的径向边接触。
  7. 根据权利要求6所述的阻尼结构，其特征在于，所述卡套的端部还设有沿径向向外延伸的挡沿，所述挡沿位于所述导向套开口端的端部。
  8. 根据权利要求6所述的阻尼结构，其特征在于，所述卡套的外侧周向排布有至少两个卡扣，所述第一槽口上开设有与所述卡扣相匹配的卡槽，所述卡扣卡合固定在所述卡槽内。
  9. 根据权利要求4所述的阻尼结构，其特征在于，在所述导向套开口端相对的一端的套壁上开设有通气孔。
  10. 一种具有上述权利要求1-9任一所述的阻尼结构的洗衣机横向减震装置，其特征在于，包括与所述阻尼结构一端铰接的第一安装座、以及竖向设置的滑杆，所述阻尼结构的另一端可滑动的套装在所述滑杆上，所述滑杆的两端分别设有第二安装座。
  11. 根据权利要求10所述的横向减震装置，其特征在于，所述阻尼结构上开设有滑孔，所述滑杆穿过所述滑孔，所述滑杆与滑孔之间设有第二缓冲垫。
  12. 根据权利要求11所述的横向减震装置，其特征在于，所述第二缓冲垫包括第二筒形主体、沿所述第二筒状主体上下两端向外延伸的第二翻边，两个所述第二翻边与第二筒形主体形成与所述滑孔边缘相匹配的容纳槽。
  13. 根据权利要求10所述的横向减震装置，其特征在于，在所述滑杆上设有上下两个限位凹槽，所述滑孔在滑杆上两个限位凹槽之间滑动。
  14. 根据权利要求10至13任一项所述的横向减震装置，其特征在于，所述第一安装座上设有销轴，所述阻尼结构上设有与所述销轴相匹配的销孔，所述销轴与销孔之间设第一缓冲垫。
  15. 根据权利要求14所述的横向减震装置，其特征在于，所述第一安装座具有平行设置的两个安装板，在两个所述安装板上分别相对设有相互靠近的销轴座，所述销孔位于两个销轴座之间，在所述销轴座上开设有销轴孔，所述销轴穿过所述销轴孔。
  16. 根据权利要求10至13任一项所述的横向减震装置，其特征在于，所述阻尼结构包括导向杆、以及套装在所述导向杆外侧的导向套，所述导向套的内侧设有与导向杆配合产生阻尼力的阻尼片，所述导向杆具有中部的空载段、以及位于空载段两端的工作段，所述空载段的直径小于所述阻尼片的内径，所述工作段的直径大于所述阻尼片的内径。
  17. 根据权利要求16所述的横向减震装置，其特征在于，所述导向杆一端位于所述导向套内，另一端套装在滑杆上；所述导向套为一端开口的筒状结构，另一端与第一安装座铰接。
  18. 一种洗衣机，包括箱体、以及位于箱体内的套装设置的外筒和内筒，所述外筒通过吊杆吊装在所述箱体上，其特征在于，在所述外筒、箱体、吊杆三者中的任意两者之间设有权利要求10至17任一项所述的横向减震装置。
  19. 根据权利要求18所述的洗衣机，其特征在于，所述第一安装座固定在外筒上，在所述箱体和外筒之间设有所述横向减震装置，两个所述第二安装座上下方向固定在箱体上。
  20. 一种洗衣机阻尼结构的设计方法，所述阻尼结构具有导向杆和阻尼片，其特征在于，所述导向杆具有中部的空载段、以及位于空载段两端的工作段；所述设计方法包括如下步骤：
    A.根据所述洗衣机自身的参数，确定洗衣机脱水时的最大偏心力Fe；进而确定阻尼结构的阻尼力F D，最终确定导向杆的工作段与阻尼片之间的过盈间距d c；
    B.根据过盈间距d c,在所述导向杆的工作段最大直径φ w和阻尼片内径φ c中，依据φ w＝φ c+2d c，在选定其中一个的尺寸后，另外一个的尺寸可以计算得出；
    C.根据阻尼片内径φ c，确定导向杆空载段直径φ z；
    D.根据洗衣机脱水稳定运行阶段外筒位移幅值d O，确定导向杆空载段的长度L z；
    E.根据导向杆空载段的长度L z、以及外筒与箱体之间的最小间距L Max，确定导向杆工作段长度L w；
    F.根据上述步骤中阻尼结构的主要参数，得到针对所述洗衣机设计的阻尼结构。
  21. 根据权利要求20所述的设计方法，其特征在于，在步骤A中，根据洗衣机脱水启动偏心质量m e、洗衣机内筒直径r 1、以及低频刚体模态的最高共振频率f PMax，计算出洗衣机脱水时的偏心力Fe＝m e*(2πf PMax) 2r I。
  22. 根据权利要求20所述的设计方法，其特征在于，在步骤A中还具有步骤A1，根据洗衣机脱水时的最大偏心力Fe，确定防撞箱平衡力F C＝s 1F e；其中s 1为安全系数。
  23. 根据权利要求22所述的设计方法，其特征在于，在步骤A中还具有位于步骤A1之后的步骤 A2，根据防撞箱平衡力F C、以及洗衣机上计划设置的阻尼结构的数量N，计算出每个阻尼结构的阻尼力为F D；阻尼力F D＝2F C/N。
  24. 根据权利要求23所述的设计方法，其特征在于，在步骤A中还具有位于步骤A2之后的步骤A3，根据阻尼结构的阻尼力为F D、以及选用的阻尼片的摩擦系数c,确定导向杆的工作段与阻尼片之间的正压力F N＝F D/c。
  25. 根据权利要求24所述的设计方法，其特征在于，在步骤A中还具有位于步骤A3之后的步骤A4，根据正压力F N、以及所述阻尼片的等效刚度k c，确定所述导向杆的工作段与阻尼片之间的过盈间距d c＝F N/k c。
  26. 根据权利要求20至25任一项所述的设计方法，其特征在于，在步骤C中，导向杆空载段直径φ z＝s 3φ c，其中s 3为安全系数，0.3<s 3≤1。
  27. 根据权利要求20至25任一项所述的设计方法，其特征在于，在步骤D中，导向杆空载段的长度L z＝2s 4d O,其中s 4为安全系数，s 4>1。
  28. 根据权利要求20至25任一项所述的设计方法，其特征在于，在步骤E中，导向杆工作段长度L w＝s 5L Max-L z/2,其中s 5为安全系数，0.2<s 5<1。
  29. 根据权利要求20至25任一项所述的设计方法，其特征在于，所述导向杆的工作段最大直径处与所述空载段之间具有锥台形过渡段。
  30. 根据权利要求20至25任一项所述的设计方法，其特征在于，所述导向杆的工作段最大直径处与所述空载段之间具有弧面形过渡段，所述弧面形过渡段的任一横截面的直径均位于所述导向杆的工作段最大直径φ w与空载段直径φ z之间。
  31. 根据权利要求20至25任一项所述的设计方法，其特征在于，所述导向杆的工作段最大直径处与所述空载段之间至少具有一段圆柱形过渡段，所述圆柱形过渡段的直径位于所述导向杆的工作段最大直径φ w与空载段直径φ z之间。
PCT/CN2017/119726 2017-07-28 2017-12-29 一种洗衣机阻尼结构及设计方法、横向减震装置及洗衣机 WO2019019553A1 (zh)

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0117824A1 (fr) * 1983-01-31 1984-09-05 Mathias Georges Martinez Système de support et d'amortissement des mouvements d'une pièce ou d'une machine
JPH11351317A (ja) * 1998-06-08 1999-12-24 Hitachi Ltd ドラム式洗濯機
KR20010025847A (ko) * 1999-09-01 2001-04-06 구자홍 세탁기
KR20080037423A (ko) * 2006-10-26 2008-04-30 삼성전자주식회사 드럼세탁기
KR20150053305A (ko) * 2013-11-07 2015-05-18 삼성전자주식회사 댐퍼 및 이를 포함하는 세탁기
WO2016148478A1 (ko) * 2015-03-16 2016-09-22 엘지전자 주식회사 세탁물 처리기기
CN205821770U (zh) * 2016-05-19 2016-12-21 无锡小天鹅股份有限公司 洗衣机

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0117824A1 (fr) * 1983-01-31 1984-09-05 Mathias Georges Martinez Système de support et d'amortissement des mouvements d'une pièce ou d'une machine
JPH11351317A (ja) * 1998-06-08 1999-12-24 Hitachi Ltd ドラム式洗濯機
KR20010025847A (ko) * 1999-09-01 2001-04-06 구자홍 세탁기
KR20080037423A (ko) * 2006-10-26 2008-04-30 삼성전자주식회사 드럼세탁기
KR20150053305A (ko) * 2013-11-07 2015-05-18 삼성전자주식회사 댐퍼 및 이를 포함하는 세탁기
WO2016148478A1 (ko) * 2015-03-16 2016-09-22 엘지전자 주식회사 세탁물 처리기기
CN205821770U (zh) * 2016-05-19 2016-12-21 无锡小天鹅股份有限公司 洗衣机

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