WO2017082674A1 - 세탁기 및 세탁기용 풀리 - Google Patents
세탁기 및 세탁기용 풀리 Download PDFInfo
- Publication number
- WO2017082674A1 WO2017082674A1 PCT/KR2016/013005 KR2016013005W WO2017082674A1 WO 2017082674 A1 WO2017082674 A1 WO 2017082674A1 KR 2016013005 W KR2016013005 W KR 2016013005W WO 2017082674 A1 WO2017082674 A1 WO 2017082674A1
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- WO
- WIPO (PCT)
- Prior art keywords
- arm
- cross
- pulley
- outer ring
- boss
- Prior art date
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Classifications
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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
- D06F37/206—Mounting of motor
-
- 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
- D06F37/02—Rotary receptacles, e.g. drums
- D06F37/04—Rotary receptacles, e.g. drums adapted for rotation or oscillation about a horizontal or inclined axis
-
- 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
- D06F37/22—Mountings, e.g. resilient mountings, for the rotary receptacle, motor, tub or casing; Preventing or damping vibrations in machines with a receptacle rotating or oscillating about a horizontal axis
-
- 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
- D06F37/30—Driving arrangements
-
- 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
- D06F37/30—Driving arrangements
- D06F37/40—Driving arrangements for driving the receptacle and an agitator or impeller, e.g. alternatively
-
- 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
- D06F58/00—Domestic laundry dryers
- D06F58/02—Domestic laundry dryers having dryer drums rotating about a horizontal axis
- D06F58/04—Details
- D06F58/08—Driving arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/02—Gearings for conveying rotary motion by endless flexible members with belts; with V-belts
-
- 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
- D06F37/30—Driving arrangements
- D06F37/36—Driving arrangements for rotating the receptacle at more than one speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/36—Pulleys
- F16H2055/366—Pulleys with means providing resilience or vibration damping
Definitions
- TECHNICAL FIELD This invention relates to the technique of suppressing the noise and the vibration which generate
- a pulley shaped to support the outer ring with a plurality of arms extending radially from the central boss is disclosed, for example, in European Patent Application Publication EP0823503A2.
- the arm of the pulley is in the form of a band plate with a constant thickness in the axial direction.
- the pulley which prevents the vibration and noise of a washing machine is disclosed by Unexamined-Japanese-Patent No. 11-114282.
- the pulley is composed of a disk-shaped inner pulley having an axial hole in the center, a ring-shaped outer pulley disposed around it, and a suction member such as rubber inserted into a gap between the inner pulley and the outer pulley. The vibration transmitted to the pulley is attenuated and absorbed by the suction member.
- a drum having a plurality of dewatering holes on an outer circumferential surface thereof is rotatably housed in a water tank.
- the drum during washing or rinsing is controlled to rotate at low speed, but it needs to be driven at high torque because a large amount of water stays, and at low torque because the drum during draining is drained. Although it is possible to do so, it is necessary to drive at high speed rotation because it uses centrifugal force.
- the motor which rotationally drives a drum requires the unique output performance from low speed high torque to high speed low torque. For this reason, in order to properly rotate and drive under such unique conditions, it is necessary to connect the shaft portion of the drum with the drive shaft of the motor as the power source at a large speed ratio, but in recent years, a direct drive type that directly drives the drum without using a complicated transmission mechanism. This is becoming common.
- the present invention relates to a washing machine in which a drum is rotatably housed inside a water tank.
- the washing machine includes a pulley attached to the shaft portion of the drum, and a motor for rotationally driving the pulley through an endless belt.
- the pulley has a ring-shaped outer ring in which the endless belt extends around the outer ring, a boss positioned at the center of the outer ring, and the shaft portion is fixed, and a plurality of arms extending radially from the boss to support the outer ring. At least a portion of the arm adjacent to the outer ring is provided with a cross-sectional surface portion in which the cross-sectional coefficient for bending in the axial direction gradually decreases from the boss toward the outer ring.
- this washing machine is a belt drive system, and the pulley of a drum is rotationally driven by a motor through the endless belt.
- the outer ring of the pulley on which the endless belt is stretched is supported by a plurality of arms extending radially from the boss, and the cross section of the outer ring side of these arms, in which the cross-sectional coefficient for axial bending gradually decreases from the boss to the outer ring.
- An addition is formed.
- the primary resonance is that the outer ring maintains its shape, and each arm is axial. In many cases, it deforms to bend in a direction. In this case, a relatively high bending stress acts on the site of the boss side of each arm.
- the structure of the arm was analyzed by the element analysis method (FEM), and by forming a cross-sectional surface portion at the outer ring side of the arm, for example, even when the weight of the arm is the same, We found that it is possible to improve the rigidity. Therefore, by providing the cross-sections on each arm, it is possible to efficiently suppress the deformation of the arm while suppressing the increase in the weight of the pulley, thereby making it possible to increase the resonance frequency in the primary resonance mode.
- FEM element analysis method
- the cross-sectional coefficient is set by gradually decreasing the height in the axial direction of the arm so that the height of the outer ring side end portion at the edge end surface portion is 30% or more and 70% or less of the height of the boss side end portion. Can be.
- the equal cross section part with a constant said cross-sectional coefficient is formed, and the length from the center of the said shaft part to the said boss side edge part is from the center of the said shaft part. You may set so that it may become 80% or less of the length to the outer edge of the said outer ring.
- the said cross-sectional coefficient can also be set by gradually reducing the thickness of the arm so that the thickness of the outer ring side edge part in the said edge end surface part may be 30% or more and 50% or less of the thickness of a boss side edge part.
- the flexural rigidity of the arm can be enhanced, so that an increase in noise due to resonance can be stably suppressed.
- the arm has a U-shaped cross section in which one side in the axial direction is opened.
- the pulley in the case where the pulley is an integrally molded product by aluminum die-casting or injection molding of a resin, the pulley can be easily taken out of the mold after molding, thereby improving productivity.
- the cross section U-shaped By making the cross section U-shaped, the weight is reduced, and the cross-sectional coefficient is increased, so that rigidity can be structurally enhanced.
- the rigidity can be improved while suppressing an increase in the weight of the pulley, and excessive noise caused by resonance can be reduced.
- 1 is a schematic longitudinal cross-sectional view showing the internal structure of the washing machine of the present embodiment.
- FIG. 2 is a schematic view of the internal structure of the washing machine viewed from the rear.
- 3A is a schematic view of the drum pulley viewed from below.
- FIG. 3B is a schematic cross sectional view taken along the line X-X in FIG. 3A.
- FIG. 4 is a schematic perspective view showing a part of the arm.
- FIG. 5 is a diagram for explaining a primary resonance of a drum pulley.
- FIG. 6 is a schematic perspective view showing a modification of the arm.
- FIG. 7A is a schematic diagram showing a model (reference example) used in structural analysis of an arm.
- 7B is a schematic diagram showing a model (example) used in structural analysis of an arm.
- FIG. 8 is a graph showing the test results of the hammer ring test. Solid lines show examples and dashed lines show reference examples, respectively.
- FIG 9 is a graph showing a result of comparing the magnitude of noise PWL in the example (solid line) and the reference example (dashed line).
- Fig. 10 is a graph showing the relationship between the ratio and the stiffness of the edge section.
- 11 is a graph showing the relationship between the amount of change in the height of the edge section and the stiffness.
- FIG. 1 and FIG. 2 the washing machine 1 which applied this invention is shown.
- This washing machine 1 is a horizontal drum-type automatic washing machine. The laundry is put into the drum 9, a button or the like is operated to instruct the washing machine 1, and a series of processing from washing to rinsing and dehydration is performed. It is configured to automatically execute.
- an inlet 4 for opening and closing the door 3 to put laundry therein is provided inside the case 2, a bottomed cylindrical water tank 5 is provided to the side.
- the water tank 5 is provided in the inside of the case 2 so that the center line C may extend in the front-back direction with the opening part facing forward.
- the opening is connected to the inlet 4 via a flexible connecting member 6.
- the water tank 5 is elastically supported by the case 2 from the up-down direction. Specifically, the water tank 5 is suspended by a plurality of coil springs 7 provided on the inner upper part of the case 2 and supported by a plurality of dampers 8 provided on the inner lower part of the case 2. . And inside the water tank 5, the bottomed cylindrical drum 9 of the size one step smaller than the water tank 5 is accommodated.
- dehydration holes 9a are formed in the peripheral wall part of the drum 9, and when dewatering, it drains out the drum 9 through these dehydration holes 9a.
- the stirring protrusion 9b which stirs the water and the laundry accommodated in the inside is formed in the several position of the inner surface of the circumferential wall part by rotating the drum 9 at the time of washing
- the drum 9 is provided in the inside of the water tank 5 so that the center may coincide with the center line C of the water tank 5 in the state which opened the opening toward the front, and the center line (C) is comprised so that rotation is possible about an axis.
- the shaft part 9c which protrudes along the center line C is formed in the center of the outer surface center of the bottom wall part of the drum 9,
- the shaft part 9c is the bearing part provided in the center of the bottom wall part of the water tank 5 It is supported by 10 so that rotation is possible.
- a protruding end portion of the shaft portion 9c protrudes outward of the water tank 5, and a pulley (drum pulley) composed of an outer ring 21, a boss 22, six arms 23, and the like protruding from the protruding end portion thereof. 20) is also integrally mounted. That is, the drum pulley 20 is mounted directly to the drum 9, so that the drum 9 and the drum pulley 20 rotate at the same rotational speed.
- the number of arms 23 is an example, It can select suitably according to the design of the drum pulley 20, such as three or seven.
- the motor 11 is provided in the lower part of the water tank 5 in the state in which the drive shaft 11a was positioned so that it might become parallel with the center line C. As shown in FIG.
- the drive shaft 11a of the motor 11 protrudes rearward from the bottom wall portion of the water tank 5, and a small diameter drive pulley 12 is fixed to the protruding end portion thereof.
- a belt also referred to as an endless belt 13
- a belt is stretched on the drive pulley 12 and the drum pulley 20 so that the drum 9 and the drum pulley 20 are driven by the motor 11. And rotationally driven through the endless belt 13.
- the drum 9 is rotated at low speed during washing or rinsing, but it is necessary to rotate the drum 9 at high speed when dewatering using centrifugal force. For this reason, the motor 11 at the time of dehydration is set so that it may control by the rotation frequency of the range of 200 Hz (12000 RPM)-300 Hz (18000 RPM), and, in the case of this washing machine 1, the motor 11 at the time of dehydration Is set to rotate at about 255 Hz.
- the outer diameter of the drum pulley 20 is relatively large in order to ensure the high torque required for washing or rinsing. For this reason, in consideration of both light weight and high rigidity, the pulley of the shape which supports the outer ring 21 with the some arm 23 is used for the drum pulley 20.
- the drum pulley 20 is an integrally molded product by aluminum die casting, resin injection molding, or the like.
- the outer ring 21 is a circular-shaped portion that looks like a long, thin strip, and its axial width Wp is set in the range of 15 to 40 mm, and its outer diameter Rp is in the range of 200 to 450 mm. Is set to.
- the former Wp is set to 21 mm and the latter Rp is set to 297 mm.
- the outer circumferential surface of the outer ring 21 is a flat surface, and the endless belt 13 hangs so as to be in close contact therewith.
- the boss 22 is a cylindrical portion located at the center of the outer ring 21, and a shaft hole 22a subjected to serration processing and a D cut is formed in the center thereof. By inserting into the shaft hole 22a, the protruding end portion of the shaft portion 9c is fixed to the boss 22 and integrated.
- the outer diameter Rb of the boss 22 is set in the range of 30-100 mm, and the height Hb of the axial direction of the boss 22 is set in the range of 15-50 mm.
- the former Rb is set to 34 mm and the latter Hb is set to 20 mm.
- the arm 23 extends radially from the outer circumferential surface of the boss 22, and its tip is integrally connected to the inner circumferential surface of the outer ring 21.
- Each arm 23 has a long thin shape having a U-shaped cross section, and has an elongated groove 23a opening along the arm 23 on one side in the axial direction.
- productivity improvement is aimed at.
- each arm 23 is devised in order to reduce the excessive noise resulting from resonance, while suppressing the increase of weight.
- part adjacent to the outer ring 21 of each arm 23 is shown.
- An end portion 24 is formed.
- the width Wa, the shape of the cross section, and the thickness t are substantially constant throughout the arm 23, and are changed by gradually decreasing only the height Ha in the axial direction.
- the cross section coefficient of the cross section 24 is set.
- edge surface part 24 may be formed in the whole arm 23, in the case of this embodiment, the height (in the axial direction) of the site
- FIG. 5 the outer ring 21 is in a state of maintaining its shape, and is often in a state of deforming each arm 23 to bend in the axial direction (primary resonance mode).
- the primary resonant frequency of the drum pulley 20 is set to be larger than 300 Hz.
- the primary resonant frequency of the drum pulley 20 is far from the rotational frequency of the motor 11 at the time of dehydration, and the increase of the noise due to resonance is suppressed.
- the cross-sectional coefficient for the deflection in the axial direction should be gradually reduced from the boss 22 toward the outer ring 21, so that the cross section is not limited to the U shape.
- an I shape, a T shape, a square frame shape, a ring shape, etc. may be sufficient.
- the shape of height, width, and a cross section are made substantially constant in the whole arm 23, and only the thickness t is gradually made small, and the cross-sectional coefficient of the edge section part 24 is shown. You can also set (to ⁇ ti). Both the height and the thickness may be gradually reduced to set the cross-sectional coefficient of the edge section 24.
- FIG. 7A is a model to which the present invention is applied (example model M2).
- Reference Example Model M1 is a shape having the same cross section from the base end (connection portion with boss 22) of arm 23 to the tip end (connection portion with outer ring 21), and the example model M2 is an arm ( 23 was made into the shape which has the back end part 25 in the base end side, and the edge end part 24 in the front end side, respectively.
- the boundary portion between the dorsal cross section 25 and the side cross section 24 was set to 30 mm from the base end of the arm 23.
- the primary resonance mode was assumed, and a load (static load) of 100 N was applied to the tip of the arm 23 as indicated by an arrow, with the base end of the arm 23 fixed.
- a load (static load) of 100 N was applied to the tip of the arm 23 as indicated by an arrow, with the base end of the arm 23 fixed.
- the weight (21g), the maximum width (17mm), and the length (100mm) are set to the same value, and under the conditions, the minimum amount of displacement of the tip of the arm 23 is the minimum.
- the optimal state was obtained and the displacement amounts of both models in that case were compared.
- the height of the tip of the arm 23 is lower than that of the reference example model M1, and the cross-sectional coefficient for the deflection in the axial direction is smaller.
- the height of the edge part (boss side edge part 24a) located in the boss 22 side of (24) became higher than the reference example model M1, and the cross-sectional coefficient with respect to the curvature to the axial direction became high.
- the displacement amount of the example model M2 was reduced by about 50% with respect to the displacement amount of the reference example model M1, so that the stiffness in the axial direction could be strengthened without performing the shape change accompanying the weight increase.
- the hammer ring test was performed using two pulleys of the same weight (Reference example pulley and Example pulley) which were tested based on the reference example model M1 and Example model M2 of an optimal state, and the resonance frequencies of these were compared. . 8, the test result is shown.
- the solid line has shown the Example pulley, and the broken line has shown the reference example pulley.
- the vibration detected the front-rear component of the axial direction.
- the primary resonant frequency of the reference pulley is 234 Hz, whereas the primary resonant frequency of the example pulley is 329 Hz, and the primary resonant frequency of the example pulley is higher than that of the reference pulley. It can be seen that the increase significantly.
- the primary resonant frequency of the pulley is a value close to the rotation frequency of the motor 11 (about 255 Hz) in the rotation frequency band of the motor 11 at the time of dehydration. Since the value is far from the rotation frequency of the motor 11 at the time of dehydration, and is far from the rotation frequency of the motor 11, an increase in noise due to resonance can be suppressed.
- Example M2 In the analysis of model M2, the relationship between the ratio and the stiffness of the edge section 24 in the arm 23 was investigated. Specifically, the weight, the maximum width, and the length are the same as those in the first embodiment, and as shown in FIG. 3A, the center C is relative to the length Lo from the center C to the outer edge of the outer ring 21. From the ratio Li / Lo (%) of the length Li to the edge part (boss side edge part 24a) which is located in the boss 22 side in the edge section 24, is changed, and each ratio Li / The optimal state in which the amount of displacement of the tip of the arm 23 at Lo was minimum was determined. The result is shown in FIG. In addition, the vertical axis
- the reduction effect was no longer confirmed when the ratio Li / Lo became 90%. From this result, it can be seen that by setting the ratio Li / Lo to be at least 80%, a stable effect of reducing the displacement amount can be obtained, and an increase in noise caused by resonance can be suppressed.
- the ratio Ho / Hi of the height Ho of the end portion (outer ring side end portion 24b) located on the outer ring 21 side with respect to the height Hi of the end portion 24a is changed to 30% or more, and the respective ratios.
- the optimum state in which the amount of displacement of the tip of the arm 23 in Ho / Hi was minimum was obtained. The result is shown in FIG.
- shaft has shown the reduction rate (% with respect to reference example model M1) of the displacement amount.
- the effect of the case where the cross-sectional coefficient of the edge section 24 was set by gradually decreasing the thickness was also investigated.
- the weight, the maximum width, and the length of the arm 23 are the same as in Example 1, and in the present analysis, the entire end of the arm 23 is the edge end portion 24 without forming the equilateral end portion 25,
- the thickness of the cross section was changed evenly, and it set so that thickness might become gradually gradually from the base end of the arm 23 to the front end.
- the ratio to / ti of the thickness to of the outer ring side end portion 24b is changed to 30% or more.
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- Main Body Construction Of Washing Machines And Laundry Dryers (AREA)
Abstract
Description
Claims (15)
- 회전 가능하게 배치되는 드럼;상기 드럼의 축부가 고정되는 보스, 상기 보스를 중심으로 하는 외륜, 상기 보스로부터 방사형으로 뻗어 상기 외륜을 지지하며, 횡단면의 크기가 변화하는 변단면부를 가지는 암을 포함하는 풀리; 및상기 풀리와 벨트로 연결되어 상기 풀리를 회전 구동하는 모터;를 포함하는 세탁기.
- 제1항에 있어서,상기 암은 횡단면의 크기가 일정한 등단면부를 포함하고,상기 변단면부는 상기 암의 외륜에 인접하는 부위에 형성되는 세탁기.
- 제1항에 있어서,상기 암은, 상기 변단면부의 횡단면의 축방향의 높이가 외륜측 단부로부터 보스측 단부를 향해 서서히 작아지도록 형성되는 세탁기.
- 제3항에 있어서,상기 암은 상기 암의 횡단면의 형상, 축방향에 수직한 폭 및 두께가 일정하게 형성되는 세탁기.
- 제3항에 있어서,상기 변단면부는 외륜측 단부의 횡단면의 축방향의 높이가 보스측 단부의 축방향의 높이의 30% 이상 70% 이하가 되도록 형성되는 세탁기.
- 제1항에 있어서,상기 외륜의 중심으로부터 상기 암의 상기 변단면부의 보스측 단부까지의 길이가 상기 외륜의 반지름의 80% 이하로 형성되는 세탁기.
- 제1항에 있어서,상기 암은 굴곡된 형상의 횡단면을 포함하고,상기 변단면부는 횡단면의 두께가 외륜측 단부로부터 보스측 단부를 향해 서서히 작아지도록 형성되는 세탁기.
- 제7항에 있어서,상기 암은, 상기 암의 횡단면의 형상, 축방향의 높이 및 축방향에 수직한 폭이 일정하게 형성되는 세탁기.
- 제7항에 있어서,상기 변단면부는 외륜측 단부의 횡단면의 두께가 보스측 단부의 횡단면의 두께의 30% 이상 50% 이하가 되도록 형성되는 세탁기.
- 제7항에 있어서,상기 변단면부는 횡단면의 축방향의 높이가 외륜측 단부로부터 보스측 단부를 향해 서서히 작아지도록 형성되는 세탁기.
- 제1항에 있어서,상기 암은 축 방향의 한 쪽에 상기 암을 따라 개구되는 홈을 포함하는 세탁기.
- 제1항에 있어서,상기 암은 U자 형상, I자 형상, T자 형상, 4각 프레임 형상, 고리 형상 중 하나의 형상을 가지는 횡단면을 포함하는 세탁기.
- 제1항에 있어서,상기 풀리는 탈수 시에 있어서의 상기 모터의 회전 주파수의 상한 값보다 큰 공진 주파수를 가지는 세탁기.
- 외륜;상기 외륜의 중심에 위치하는 보스; 및상기 보스로부터 방사형으로 뻗어 상기 외륜을 지지하며, 횡단면의 크기가 변화하는 변단면부를 포함하는 암;을 포함하는 세탁기용 풀리.
- 제14항에 있어서,상기 암의 상기 변단면부는 축방향으로의 휨에 대한 단면 계수가 상기 보스로부터 상기 외륜을 향해 서서히 작아지도록 형성되는 세탁기용 풀리.
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KR1020187005030A KR102596936B1 (ko) | 2015-11-13 | 2016-11-11 | 세탁기 및 세탁기용 풀리 |
US15/775,976 US11131051B2 (en) | 2015-11-13 | 2016-11-11 | Washing machine and pulley for washing machine |
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JP2015-223243 | 2015-11-13 | ||
JP2015223243A JP2017086686A (ja) | 2015-11-13 | 2015-11-13 | 洗濯機 |
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WO2017082674A1 true WO2017082674A1 (ko) | 2017-05-18 |
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PCT/KR2016/013005 WO2017082674A1 (ko) | 2015-11-13 | 2016-11-11 | 세탁기 및 세탁기용 풀리 |
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US (1) | US11131051B2 (ko) |
JP (1) | JP2017086686A (ko) |
KR (1) | KR102596936B1 (ko) |
WO (1) | WO2017082674A1 (ko) |
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EP3615844B1 (en) * | 2017-05-25 | 2022-01-12 | Zhejiang Dahua Technology Co., Ltd | Belt driven system |
DE102019212954A1 (de) | 2019-08-28 | 2021-03-04 | BSH Hausgeräte GmbH | Wäschepflegegerät mit einer Riemenscheibe |
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2016
- 2016-11-11 US US15/775,976 patent/US11131051B2/en active Active
- 2016-11-11 WO PCT/KR2016/013005 patent/WO2017082674A1/ko active Application Filing
- 2016-11-11 KR KR1020187005030A patent/KR102596936B1/ko active IP Right Grant
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Also Published As
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US20180327955A1 (en) | 2018-11-15 |
KR20180071246A (ko) | 2018-06-27 |
KR102596936B1 (ko) | 2023-11-03 |
JP2017086686A (ja) | 2017-05-25 |
US11131051B2 (en) | 2021-09-28 |
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