WO2018221870A1

WO2018221870A1 - Laundry treatment device

Info

Publication number: WO2018221870A1
Application number: PCT/KR2018/005397
Authority: WO
Inventors: 최기훈; 안기용; 박민호
Original assignee: 엘지전자 주식회사
Priority date: 2016-07-07
Filing date: 2018-05-10
Publication date: 2018-12-06

Abstract

A laundry treatment device according to an embodiment of the present invention comprises: a cabinet; a drum received inside the cabinet; a tub in which the drum is received; and a dynamic absorber provided for absorbing a vibration of the cabinet, wherein the dynamic absorber comprises: a support plate coupled to the cabinet; and a mass body placed movably on the support plate to absorb a vibration transferred to the cabinet, and the support plate has a partition wall protruding from the upper surface thereof to partition the upper surface of the support plate, on which the mass body is placed, into a first reception part and a second reception part.

Description

Laundry treatment unit

The present invention relates to a laundry treatment apparatus.

In the case of a home appliance having a drum rotating therein, such as a washing machine or a dryer, as the rotational speed (rpm) of the drum increases, the laundry force introduced into the drum, that is, the horizontal force is generated by the eccentricity of the load. do.

In particular, as in the dehydration process, in the process of increasing the rotational speed of the drum, a transient vibration occurs in which the horizontal vibration displacement of the cabinet rapidly increases at the resonant frequency point of the washing machine cabinet. In addition, when the drum is kept constant at the highest speed, a normal vibration occurs in which the same vibration is constantly repeated.

Due to such excessive vibration, the washing machine whistle in the left and right directions in the process of increasing the rotation speed of the drum occurs. And such transient vibrations are more pronounced in stack type washing machines where the washing machine is spaced from the ground.

For example, in the case of a stack type washing machine stacked on the upper surface of a small washing machine or an object for storing laundry, the vibration displacement of the transient vibration is larger than that of the general washing machine directly placed on the installation surface, and the excessive vibration occurs in the low speed operation. That is, the stack type washing machine has a faster time to generate excessive vibration than the washing machine placed directly on the floor.

In order to absorb such excessive vibration, a dynamic absorber is generally installed in the washing machine.

The copper reducer is a copper reducer using the principle of absorbing the vibration of the washing machine by vibrating in the horizontal direction in a phase opposite to the phase of the horizontal excitation force generated by the rotation of the drum 180 degrees.

In detail, when the drum accelerates and rotates, as described above, the excitation force is generated in the horizontal direction by the rotation of the eccentric load (laundry). When the drum reaches the resonance frequency of the drum while the rotation speed of the drum increases, the washing machine cabinet performs a harmonic vibration with the excitation force and the phase difference of 90 degrees.

In addition, at the resonance point, the copper reducer is subjected to harmonic vibration with a phase difference of 90 degrees from the vibration of the washing machine cabinet. As a result, the excitation force and the copper reducer vibrate in opposite directions with a phase difference of 180 degrees, and the vibration is canceled. As a result, the washing machine cabinet does not move.

In the following US registered patent, a technique is disclosed in which the copper reducer is provided in a washing machine.

The prior art copper reducer has a structure in which a frame is provided on a bottom of a casing of a washing machine, a viscoelastic member is placed on an upper surface of the frame, and a mass body for vibration absorption is placed on an upper surface of the viscoelastic member.

This copper reducer structure has the following problems.

First, since the viscoelastic member is placed on the bottom of the mass body, the load of the mass body continuously acts on the elastic member, resulting in breakage of the elastic member and deterioration of performance.

Second, when the mass vibrates in the horizontal direction, the viscoelastic member absorbs vibration by using shear stress acting in the left and right directions, and thus has a disadvantage in that the damping ratio is not effectively absorbed due to low damping ratio.

The patent specification of the prior art describes that the vibration can be effectively absorbed in the entire rotational speed region of the drum, but the copper reducer disclosed in the prior art may have an effect of absorbing the continuous oscillation. The ability to absorb transient vibrations in which the vibration displacement suddenly increases is significantly lower.

Third, since shear stress acts alternately on the viscoelastic member, there is a disadvantage that the breakage of the viscoelastic member is increased and the life is shortened.

Fourth, when the horizontal vibration acts on the washing machine and the mass moves horizontally in the opposite direction to the vibration, the elastic member is bent while the upper end of the elastic member moves in the horizontal direction. As a result, a problem arises in that the mass cannot swing in the left and right directions while maintaining a horizontal state for vibration absorption. In other words, when the mass swings in the left and right directions to absorb the lateral vibration, a phenomenon in which the left end and the right end of the mass are inclined downward due to the bending phenomenon of the elastic member. As a result, the horizontal vibrations acting on the washing machine cannot be absorbed effectively.

Prior Art: US Patent US8443636 (May 21, 2013)

The present invention has been proposed to improve the above problems.

Laundry treatment apparatus according to an embodiment of the present invention for achieving the above object, the cabinet; A drum housed in the cabinet; A tub for receiving the drum; And a copper reducer provided to absorb vibration of the cabinet.

The copper reducer may include: a support plate coupled to the cabinet; And a mass body movably placed on the support plate to absorb vibrations transmitted to the cabinet.

The partition wall partitioning the upper surface of the support plate on which the mass is placed into the first and second receiving portions is formed to protrude from the upper surface of the support plate.

According to the laundry treatment apparatus according to the embodiment of the present invention constituting the above configuration has the following effects.

First, the copper reducer according to the embodiment of the present invention is provided in the laundry treatment apparatus, thereby effectively absorbing various types of vibrations generated in the cabinet of the laundry treatment apparatus. In other words, by providing a mass for absorbing the transient vibration and a mass for absorbing the normal vibration, respectively, it is possible to absorb not only the transient vibration occurring in the low frequency (low rotation) region but also the normal vibration occurring in the high frequency (high rotation) region. There are advantages to it.

Second, the dynamic reducer is designed such that the second half of the mass absorbing the transient vibration and the first half of the mass absorbing the normal vibration overlap so that the mass absorbing the normal vibration partially contributes to absorbing the transient vibration. The advantage is that the amplitude increases.

In other words, there is an advantage of reducing the vibration displacement of the secondary transient vibration appearing in the second half of the two secondary transient vibrations that are small after the transient vibration absorption.

Third, by overlapping the latter part of the suction region of the transient vibration with the first part of the suction region of the normal vibration, the vibration displacement of the secondary transient vibration is significantly lowered, and as a result, the vibration displacement of the normal vibration is reduced, and the absorption capability of the normal vibration is improved. There is.

1 is a perspective view of a laundry treatment apparatus according to an embodiment of the present invention.

Figure 2 is an exploded perspective view of the laundry treatment apparatus having a copper reducer according to an embodiment of the present invention.

3 is a perspective view of a copper reducer according to an embodiment of the present invention.

4 is an exploded perspective view of the copper reducer;

5 is a perspective view of a support plate constituting the copper reducer according to the embodiment of the present invention.

6 is a plan view of the support plate.

7 is a longitudinal sectional view taken along line 7-7 of FIG.

8 is a plan view of a first mass in accordance with an embodiment of the present invention.

9 is a perspective view of the first mass;

10 is a view showing a buffer structure against the vertical vibration of the first mass in accordance with an embodiment of the present invention.

11 is a longitudinal sectional view taken along line 11-11 of FIG. 10;

12 is a cross-sectional view showing a separation prevention structure for preventing the mass from being separated from the support plate during the transport of the laundry treatment apparatus.

13 is a perspective view of a second mass in accordance with an embodiment of the present invention.

14 is a top perspective view of the supporter according to the embodiment of the present invention.

15 is a bottom perspective view of the supporter;

16 is an exploded perspective view of the supporter;

17 is a longitudinal sectional view taken along the line 17-17 of FIG. 14;

18 is a top perspective view of the upper slider constituting the slider according to the embodiment of the present invention;

19 is a bottom perspective view of the upper slider;

20 is a plan perspective view of a lower slider constituting the slider;

21 is a bottom perspective view of the lower slider;

FIG. 22 is a longitudinal sectional view taken along the line 22-22 of FIG. 3; FIG.

23 is a top perspective view of a second elastic damper in accordance with an embodiment of the present invention.

24 is a bottom perspective view of the second elastic damper;

25 is a top perspective view of the first elastic damper according to the embodiment of the present invention.

Fig. 26 is a bottom perspective view of the first elastic damper.

27 is a longitudinal sectional view taken along the line 27-27 of FIG. 25;

28 is a graph showing vibration displacement of a laundry treatment apparatus equipped with a copper reducer including only a mass for transient vibration absorption.

29 is a graph showing the vibration displacement of the laundry treatment apparatus equipped with a copper reducer according to an embodiment of the present invention.

Hereinafter, a laundry treatment apparatus according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

First, the terms described in the present invention are defined.

The transient oscillation (vibration) or transient oscillation (vibration) described below is a vibration in which the vibration displacement of the cabinet increases sharply at the resonance point of the drum when the drum to which the laundry is put is accelerated for rinsing or dehydration. It is defined as meaning.

In addition, steady-state oscillation (vibration) or continuous oscillation (vibration), which will be described below, is defined as meaning vibration that occurs continuously with almost constant vibration displacement while the drum is maintained at the highest speed. do.

In addition, the dynamic reducer according to the embodiment of the present invention improves or absorbs the transient vibration or the normal vibration, wherein the dynamic reducer eliminates or minimizes the vibration displacement of the transient vibration or the normal vibration, thereby minimizing vibration of the cabinet. Can be understood.

1 is a perspective view of a laundry treatment apparatus according to an embodiment of the present invention, Figure 2 is an exploded perspective view of the laundry treatment apparatus having a copper reducer according to an embodiment of the present invention.

1 and 2, in the embodiment of the present invention, the turbidity treatment apparatus 10 includes a cabinet 11 and a copper reducer that absorbs vibrations transmitted to the cabinet by being placed on an upper surface of the cabinet 11. 20 and a drum (not shown) accommodated in the cabinet 11 and a tub 16 for accommodating the drum.

In detail, the cabinet includes a front cabinet 111, a side cabinet 112, and a rear cabinet 113. A top plate 12 is placed on the top surface of the cabinet to cover the top opening of the cabinet 11.

In addition, the door 15 is rotatably coupled to the front cabinet 111 to inject laundry into the drum. In addition, a detergent box 14 and a control panel 13 may be provided at an upper end of the front cabinet 111.

In addition, the laundry treatment apparatus 10 may be directly placed on the installation surface, or may be placed on a separate stack W having a predetermined height h. The separate stack W may be an independent laundry device having a small volume, or may be a storage box for storing an object including laundry, but is not limited thereto.

On the other hand, the dynamic absorber (dynamic absorber) 20 according to the embodiment of the present invention is seated on the upper surface of the cabinet 11, is covered by the top plate 12 to block the external exposure.

In addition, the left and right ends of the copper reducer 20 are seated on top of the left and right side cabinet 112. In addition, since the detergent box 14 and the control panel 13 are positioned inside the cabinet 11, the copper reducer 20 is disposed at the front end of the cabinet 11 in order to avoid interference therewith. It may be located spaced rearward from the part.

For example, the horizontal distance between the front end of the support plate 24 and the front cabinet 111 may be set longer than the horizontal distance between the rear end of the support plate 24 and the rear cabinet 113. have. However, the present invention is not necessarily limited thereto, and the copper reducer 20 may be located at the center of the upper surface of the cabinet 11.

Hereinafter, the structure and function of the copper reducer 20 will be described in more detail with reference to the accompanying drawings.

Figure 3 is a perspective view of a copper reducer according to an embodiment of the present invention, Figure 4 is an exploded perspective view of the copper reducer.

3 and 4, the copper reducer 20 according to the embodiment of the present invention includes a support plate 21 and a moving mass 22 slidably placed on the support plate 21. And it may include an elastic damper 25 provided on the side of the mass body 22, and a sliding guide member for supporting the bottom surface of the mass body 22.

In detail, the mass 22 is slidably placed on the support plate 21 in a horizontal direction, specifically, in the left and right directions of the laundry treatment apparatus 10. The mass 22 may include a first mass 23 and a second mass 24 placed on the rear side of the first mass 23. Here, it is clear that the front mass may be defined as the first mass, and the rear mass may be defined as the first mass.

In addition, any one of the first and second

mass bodies

23 and 24 is a damper for absorbing the transient vibration of the cabinet 11, and the other is a damper for absorbing the normal vibration of the cabinet 11. . And, the damper for absorbing the transient vibration may be placed in front of the damper for absorbing the normal vibration, or may be placed in the rear.

In the present embodiment, the front first mass body 23 is a damper for reducing normal vibration, and the rear second mass body 23 is a damper for reducing transient vibration. In addition, the mass of the damper for reducing the normal vibration may be greater than the mass of the damper for reducing the transient vibration. The reason is that the normal vibration occurs at high speed rotation, and the transient vibration occurs at relatively low speed rotation than the normal vibration.

The elastic damper 25 may include a first elastic damper 25 supporting both side surfaces of the first mass body 23 and a second elastic damper 25 supporting both side surfaces of the second mass body 24. 27). The elastic damper 25 is made of a material having a predetermined elasticity and attenuation, and absorbs the shock generated when the mass body 22 moves in the horizontal direction in a phase opposite to the excitation force of the drum. That is, the elastic damper 25 prevents the mass 22 from directly hitting the side surface of the support plate 21 and simultaneously pushes the mass 25 in the opposite direction by an elastic force. .

On the other hand, the sliding guide member includes a supporter 28 and a slider 29.

In detail, the supporter 28 is disposed on the bottom of the damper for reducing normal vibration, and the slider 29 is disposed on the bottom of the damper for transient vibration. Therefore, in the present embodiment, the supporter 28 may be disposed under the first mass body 23, and the slider 29 may be disposed under the second mass body 24. Here, the smaller the damping of the mass is advantageous to improve the normal vibration, and the larger the damping of the mass is advantageous to improve the transient vibration. Therefore, the attenuation of the supporter 28 is designed to be minimal, and the attenuation of the slider 29 is designed to be considerably larger than the attenuation of the supporter 28, but the resonance frequency at which the transient vibration occurs and the second mass 24 ) Is appropriately selected in consideration of the mass and the like.

Hereinafter, each component constituting the copper reducer 20 will be described in detail with reference to the accompanying drawings.

5 is a perspective view of a support plate constituting the copper reducer according to the embodiment of the present invention, FIG. 6 is a plan view of the support plate, and FIG. 7 is a longitudinal cross-sectional view taken along 7-7 of FIG. 6.

5 to 7, the support plate 21 constituting the copper reducer 20 according to the embodiment of the present invention is a support member for supporting the mass 22, the mass 22 is left and right It is placed to be slidable in the direction.

In detail, the support plate 21 may include a plate body 211 made of a rectangular metal plate, an outer wall 212 enclosed in a substantially rectangular shape at an outer edge of the plate body 211, and The partition wall 213 extending a predetermined length from the inner side of the outer wall 212 to the left and right sides, and the cabinet coupling part 215 extending from the outer edge of the outer wall 212 and seated on an upper surface of the side cabinet 112. ) May be included.

In more detail, the outer wall 212 and the partition wall 213 protrude a predetermined height from an upper surface of the plate body 211 by a forming process to reinforce the rigidity of the support plate 21. In addition, a mass body accommodating part 214 in which the mass 22 is accommodated is formed inside the outer wall 212. The protruding height of the outer wall 212 and the partition wall 213 may be in the range of 1mm to 15mm. However, the present invention is not limited thereto, and it is sufficient to form at least the thickness of the mass body 22.

In addition, the partition wall 213 partitions the mass receiving portion 214 into a first receiving portion 214a in the front and a second receiving portion 214b in the rear. The left and right ends of the partition wall 213 may extend to the inner edge of the outer wall 212, and as shown, both ends may be spaced a predetermined distance from the inner edge of the outer wall 212. Can be.

In the present embodiment, since the first mass 23 has a larger mass (or weight) than the second mass 24, the partition wall 213 is later than the front end of the outer wall 212. It may be located closer to the end.

Meanwhile, a plurality of cabinet coupling parts 215 may be formed at each of left and right edges of the plate body 211. In addition, one or more fastening holes 215a may be formed in each cabinet coupling part 215. A fastening member such as a screw penetrates through the fastening hole 215a and is inserted into an upper surface of the side cabinet 112.

In addition, an avoidance groove 215b may be formed between the cabinet coupling parts 215 adjacent in the front and rear directions. By forming the avoidance groove 215b, it is possible to prevent an obstacle such as a ground wire or a bolt head coupled to the upper surface of the side cabinet 112 from interfering with the support plate 21.

In addition, a plurality of strength reinforcement parts 217 are formed at portions of the plate body 211 corresponding to the mass receiving part 214, and the plurality of strength reinforcement parts 217 are formed by the forming process. The lower surface of the body 211 may be formed with a predetermined depth downward. In addition, the plurality of strength sub-cavities 217 may be spaced apart from each other in the front-rear direction.

In detail, the plurality of strength reinforcing parts 217 may include a plurality of first forming parts 217a (or first strength reinforcing parts) and the second receiving parts (not shown) formed in the first accommodating part 214a. 214b) may include a plurality of second forming portions 217b (or second strength reinforcing portions) formed in the region.

In addition, left and right edges of the plurality of first forming parts 217a are connected to inner edges of the outer wall 212, and front ends of the forming parts formed at the foremost of the plurality of first forming parts 217a. It may be connected to the inner edge of the outer wall (212).

In addition, left and right edges of the plurality of second forming parts 217b may be spaced apart from the inner edges of the outer wall 212 by a predetermined distance. In addition, a front end of the forming part formed at the foremost of the plurality of second forming parts 217b may be connected to the partition wall 213. The rear end of the forming part formed at the rearmost part of the plurality of second forming parts 217b may be connected to an inner edge of the outer wall 212.

In addition, a plurality of avoidance holes 218a may be formed in the plurality of strength reinforcement parts 217. The plurality of avoidance holes 218a are holes for preventing interference with the head of the fastening member protruding from the bottom of the mass 22, for example, the head of the rivet. In addition, since the mass 22 reciprocates in the left and right directions, each of the avoidance holes 218a may have an ellipse or a long hole shape having a long side portion corresponding to a moving distance (displacement) of the mass 22.

In addition, one or more drainage holes may be formed in the plate body 211 corresponding to the mass accommodating part 214, so that moisture formed in the copper reducer 20 may be quickly discharged to the outside.

In addition, a supporter mounting part 219 may be formed in any one of the plurality of first forming parts 217a. The formation position of the supporter mounting portion 29 is determined according to the mounting position of the supporter 28. In this embodiment, two supporter mounting portions 219 are spaced apart from each other in the left and right directions of the support plate 21.

The supporter mounting portion 219 includes a roller hole 219a, a pair of hook holes 219c formed at the front and the rear of the roller hole 219a, and the roller holes 219a and the hook hole 219c. It may include a pair of roller shaft support (219b) formed between the).

In addition, a plurality of slider fastening holes 218b may be formed in the second forming part 217b. The slider fastening hole 218b is a hole for fixing the slider 29 to the support plate 21.

Meanwhile, a plurality of fastening slits 216 may be formed at each of the left and right edges of the mass receiving part 214.

In detail, the plurality of fastening slits 216 are formed at points adjacent to the inner edge of the outer wall 212, and the plurality of elastic dampers 25 are fitted to the plurality of fastening slits 216. .

Each of the plurality of fastening slits 216 may have a T-shape or an I-shape including a long side portion and a short side portion formed in a direction crossing the long side portion at an end portion of the long side portion. Since the fastening slit 216 is formed in a T-shape or an I-shape, a fastening box (described later) protruding from the bottom surface of the elastic damper 215 may be easily inserted. A method of inserting the fastening arm of the elastic damper 215 into the fastening slit 216 will be described below with reference to the drawings.

In addition, since the support plate 21 is fixed to the upper surface of the side cabinet 112, the vibration of the cabinet 11 is transmitted to the support plate 21, it can be vibrated with the cabinet (11). .

Here, the first mode resonant frequency of the support plate 21 is formed to be greater than the maximum rotation frequency of the drum, it is possible to avoid the self-resonance of the support plate 21 in the rotation section of the drum. As an example, the primary mode natural frequency (or primary mode resonance frequency) of the support plate 21 may be in a range of 20 Hz to 30 Hz.

8 is a plan view of a first mass according to an embodiment of the present invention, and FIG. 9 is a perspective view of the first mass.

8 and 9, the first mass body 23 absorbing the normal vibration of the mass body 22 according to the embodiment of the present invention may have a rectangular shape with rounded corners.

In detail, the first mass body 23 may be made of a metal material having a high density to secure sufficient mass in a limited space inside the cabinet 11. The first mass 23 may be a single mass by casting, or may be formed by stacking a plurality of thin metal plates.

When the first mass 23 is formed by stacking a plurality of metal thin plates, the plurality of metal thin plates are combined into a single body by the rivet part 231. In addition, four corners of the mass 22 are illustrated as being rounded, but are not necessarily limited thereto. In addition, the number of the rivets 231 may be appropriately set according to the number and size of the metal thin plates to be stacked, so that a plurality of metal thin plates may function like a single mass without shaking or friction.

In addition, a plurality of guide hole units may be formed in the central portion of the first mass 23. Each of the guide hole units may include a plurality of guide holes 233.

The plurality of guide hole units may be disposed on a line that bisects the first mass 23 in the front-rear direction, and is symmetrical to the left and right sides based on a line that bisects the first mass 23 in the left-right direction. Can be placed in the position.

The guide hole unit is a portion in which the supporter 28 to be described later is mounted, and the supporter 28 can stably move while maintaining the horizontal state of the first mass 23. A single guide hole unit may be formed at the center of the mass body 23, but in this case, the first mass body 23 may be tilted in the vertical direction while reciprocating in the left and right directions to interfere with the support plate 21. Can be. Therefore, at least two guide hole units may be formed. In this embodiment, it is shown that two guide hole units are disposed on the left and right sides of the mass 23, respectively.

The guide hole 233 constituting the guide hole unit may have a long hole shape having a long side portion and a short side portion, and the length d of the long side portion of the guide hole 233 may be defined by the mass body 23. Corresponds to the displacement. That is, when the horizontal vibration is transmitted to the cabinet 11, the first mass 23 may swing in the horizontal direction by the length of the guide hole 233.

On the other hand, the first mass 23 swings horizontally in the horizontal direction, but is not without vibration in the vertical direction. When a vertical vibration is applied to the first mass 23, an upper surface of the first mass 23 may strike the top plate 12 to cause noise. To prevent this, the buffer pad 234 may be separately attached to the upper surface of the first mass 23.

The shock absorbing pad 234 is also attached to the bottom surface of the first mass body 23 so that the center portion of the first mass body 23 sags due to the load or the vertical direction acting on the vibration first damper 23. By vibrating, the mass 23 can be prevented from directly hitting the support plate 21. The buffer pad 234 may include a nonwoven fabric, a viscoelastic member, silicon, or the like.

It is noted that the buffer pad 234 may be mounted on at least one of an upper surface and a lower surface of the second mass body 23 to be described later.

In addition, one or more buffer member holes 232 may be formed in the first mass body 23, and the buffer member holes 232 will be described in detail with reference to the accompanying drawings. The buffer member hole 232 may also be formed in the second mass 24.

10 is a view showing a buffer structure against the vertical vibration of the first mass according to an embodiment of the present invention, Figure 11 is a longitudinal cross-sectional view taken along 11-11 of FIG.

10 and 11, the buffer member hole 232 may be formed in the first mass 23, and the buffer pin 235 may be inserted into the buffer member hole 232.

In detail, the buffer pin 235 may include a pin body 235a having an outer diameter corresponding to the diameter of the buffer member hole 232, and an upper buffer part 235b formed at an upper end of the pin body 235a. The lower buffer part 235c formed at the lower end of the pin body 235a may be included.

In more detail, at least the upper buffer portion 235b and the lower buffer portion 235c of the buffer pin 235 may be made of the same material as the buffer pad 235. The outer diameter of the lower buffer part 235c may be larger than the outer diameter of the pin body 235a, and the upper end of the upper buffer part 235b may be spaced apart from the bottom surface of the top plate 12. It may be formed higher than the upper surface of the first mass (23).

In the state where the buffer pin 235 is coupled to the first mass 23, the lower buffer part 235c is spaced apart from the upper surface of the support plate 21.

Here, the upper buffer portion 235b may be provided as a separate component having an outer diameter larger than the diameter of the buffer member hole 232 and may be fastened to an upper end of the pin body 235a. In this case, the lower buffer part 235c may be formed as a single body with the pin body 235a.

Alternatively, the upper buffer portion 235b and the pin body 235a is made of one body, and the lower buffer portion 235b is made of a separate member is fastened to the bottom of the pin body 235a It is possible.

As such, when the shock absorbing pin 235 is inserted into the shock absorbing member hole 232, when the vibration in the vertical direction does not act on the first mass body 23, the upper and lower ends of the shock absorbing member 235 may be formed. It does not touch the top plate 12 and the support plate 21. That is, only when the vertical vibration acts on the first mass 23, the upper end and the lower end of the buffer pin 235 intermittently touch the top plate 12 and the support plate 21.

Note that the structure of the buffer pin 235 may be provided to the second mass 24 in the same manner.

The separation prevention structure can be equally applied to the second mass as well as the first mass.

Referring to FIG. 12, at least one through-hole 220 having a long hole shape having the same shape as the guide hole 233 (see FIG. 8) may be formed in the mass body 22. That is, the through hole 220 may have a long side portion and a short side portion having the same length as the long side portion and the short side portion of the guide hole 233. In detail, the long side length d of the guide hole 233 may be the same as the long side length of the through hole 220.

In addition, a fastening member V such as a bolt may pass through the through hole 220. The fastening member V may be inserted into and fixed to the support plate 21 through the through hole 220 from the upper surface of the mass body 22. The body of the fastening member V accommodated in the through hole 220 may have the same diameter as that of the guide boss (to be described later) of the supporter 28 fitted into the guide hole 233.

In addition, the outer diameter of the head portion of the fastening member V is at least greater than the length of the short side of the through hole 220, so that the mass body 22 is separated from the fastening member V in the process of vibrating. Can be prevented.

According to the above structure, even when the laundry treatment apparatus 10 is inverted or turned sideways in the process of transporting the laundry treatment apparatus 10 equipped with the copper reducer 20, the mass body 22 Is not separated from the support plate 21.

In addition, the length of the long side portion of the through hole 220 is formed to have the same length as the length of the long side portion of the guide hole 233, so that the mass body 22 swings in the horizontal direction to absorb the vibration of the cabinet 11. It does not act as an obstacle in the process. That is, the phenomenon that the fastening member V hits the mass 12 does not occur. That is, the mass 22 is limited to the maximum vibration displacement in the horizontal direction by the elastic damper 25, the length of the long side portion (d) of the through hole 220 is the maximum vibration displacement of the mass 12 This is because it is formed larger.

Referring to FIG. 13, the second mass 24 according to the embodiment of the present invention is mainly provided to absorb the transient vibration acting on the cabinet 11.

In detail, the second mass 24 has a mass smaller than the first mass 24 and at a rotational speed lower than the rotational speed (or rotational frequency) of the drum on which the first mass 23 operates. Works.

The second mass 24 may also have a rectangular shape with rounded corners, similar to the first mass 23, and may have a structure in which a single mass of a metal material or a plurality of thin metals are stacked.

In addition, when the mass 24 is formed by stacking a plurality of thin metals, the plurality of thin metals may be combined into a single body by the rivet part 241.

Meanwhile, a plurality of sliders 29 may be mounted on the bottom surface of the second mass 24, and a plurality of slider fastening holes 242 may be formed in each of the portions on which the sliders 29 are mounted.

14 is a top perspective view of the supporter according to the embodiment of the present invention, FIG. 15 is a bottom perspective view of the supporter, FIG. 16 is an exploded perspective view of the supporter, and FIG. 17 is a longitudinal cross-sectional view taken along the 17-17 of FIG. 14. It is also.

14 to 17, the supporter 28 according to the embodiment of the present invention is provided on the bottom of the mass for normal vibration absorption.

In detail, the supporter 28 is installed on the bottom surface of the first mass body 23, and minimizes the generation of frictional force when the first mass body 23 vibrates in the left and right directions, thereby generating a steady state generated in the high speed rotation region. Maximize the absorption of vibration.

In addition, the supporter 28 functions to prevent the first mass body 23 from sagging due to its own weight and to vibrate the first mass body 23 in the horizontal direction as much as possible.

The supporter 28 may include a roller support part 282 fixed to the supporter mounting part 219 of the support plate 21, and a guide roller 281 rotatably seated on the roller support part 282. have.

The guide roller 281 includes a roller 281a and a roller shaft 281b penetrating the center of the roller 281a. The roller 281a is in linear contact with the bottom face of the first mass body 23 to rotate together with the first mass body 23. Although the guide roller 281 is provided to minimize the frictional force generated between the first mass 23 and the supporter 28, a ball bearing which is in point contact with the first mass 23 may be applied. Reveal.

In addition, the roller support 282 is a pair of seating plate 282a which is seated on the upper surface of the support plate 21, and at least one pair extending downward from the front end and the rear end of the seating plate 282a, respectively. It may include a fastening hook 282e, a receiving hole formed in the center of the seating plate 282a, and a plurality of guide bosses 282b protruding a predetermined length from the top surface of the seating plate 282a.

In detail, the fastening hooks 282e are provided to extend one by one at the front end and the rear end of the seating plate 282a, but the present invention is not limited thereto, and a plurality of fastening hooks 282e may be formed at each of the front end and the rear end.

In addition, the guide boss 282b is also proposed to protrude two at the left and right edges of the seating plate 282a, respectively, but is not limited thereto, and may be protruded one at each of the left and right edges. The guide boss 282b is inserted into the guide hole 233 of the first mass 23. Therefore, the guide hole 233 may be formed in a number corresponding to the number of the guide boss 282b. When the first mass 23 vibrates in the left and right directions, the guide boss 282b relatively moves in the left and right directions inside the guide hole 233. The diameter of the guide boss 282b may be formed to a size corresponding to the length of the short side portion of the guide hole 233.

In addition, the receiving hole extends in the front-rear direction from the center of the seating plate 282a to the roller shaft receiving hole 282d for accommodating the roller shaft 282b, and the left and right directions at the center of the seating plate 282a. It may include a roller receiving hole (282c) extending to accommodate the roller (281a).

As shown in FIG. 15, shaft support ribs 282f may protrude from the bottom left and right edges of the roller shaft accommodation hole 282d, respectively. In detail, a pair of axial support ribs 282f extending at the points facing each other are formed at the front end point and the rear end point of the roller receiving hole 282c, respectively, and are located at the front of the roller 281a. The roller shaft portion 281b and the rear roller shaft portion can be supported, respectively. In addition, as shown in FIG. 17, the roller shaft 281b is not only supported by the shaft support ribs 282f, but also the roller shaft rounded in an arc shape on the support plate 21. It is also supported by the support part 219b.

Further, rocking prevention ribs 282g extend on the bottoms of the left and right ends of the roller accommodation holes 282c, respectively. The pair of rocking prevention ribs 282g may be caught by the left and right ends of the roller hole 219a formed in the support plate 21 to prevent the mounting plate 282a from shaking in the left and right directions. have. If the rocking prevention rib 282g is not present, the fastening force of the pair of fastening hooks 282e should be quite large. However, since the rocking prevention rib 282g is formed, the pair of fastening hooks 282e is sufficient only to hold the support plate 21, and the phenomenon in which the seating plate 282a swings in the left and right directions is as follows. This is prevented by the rocking prevention rib 282g.

18 is a top perspective view of an upper slider constituting a slider according to an embodiment of the present invention, FIG. 19 is a bottom perspective view of the upper slider, FIG. 20 is a top perspective view of a lower slider constituting the slider, and FIG. 21 is A bottom perspective view of the lower slider, and FIG. 22 is a longitudinal cross-sectional view taken along the line 22-22 of FIG.

18 to 22, the slider 29 according to the embodiment of the present invention is mounted on the bottom surface of the mass absorbing the transient vibration. Therefore, the slider 29 may be disposed on the bottom surface of the second mass 24.

In detail, the slider 29 has a form in which the upper slider 30 and the lower slider 31 are coupled, and the upper slider 30 and the lower slider 31 slide with respect to each other with a predetermined friction damping. Move.

The second mass 24 absorbs the transient vibration generated at the resonance point of the drum by the magnitude of the friction damping of the slider 29. The excessive vibration absorption region (or the absorption width) is determined by the magnitude of the friction damping and the mass of the second mass 24.

In detail, the upper slider 30 includes an upper slider body 301 having a substantially rectangular shape, a plurality of fastening protrusions 302 protruding from four corner portions of the upper surface of the upper slider body 301, and the upper slider. A plurality of slider rails 303 protruding from the bottom of the body 301 and extending in the longitudinal direction of the upper slider body 301 may be included.

In more detail, the plurality of fastening protrusions 302 may be inserted into the plurality of slider fastening holes 242 formed in the second mass 24. The slider fastening hole 242 may be formed in the second mass 24 in a number corresponding to the number of the fastening protrusions 302.

In addition, the plurality of slider fastening holes 242 corresponding to the number and positions of the fastening protrusions 302 may form one slider fastening hole group. In addition, a plurality of slider fastening hole groups may be formed in the second mass 24 so that the upper slider 30 may be coupled to the bottom surface of the second mass 24 at various positions.

The fastening protrusion 302 may protrude to four corner portions of the upper surface of the upper slider body 301, but is not limited thereto. As another example, in the form of a three-point support, one fastening protrusion protrudes from the center of one edge of the upper surface of the upper slider body 301, and a fastening protrusion may protrude from two edges of opposite edges, respectively.

Alternatively, two or more fastening protrusions may be arranged in one row in the width direction at the center of the upper surface of the upper slider body 301, or two or more fastening protrusions may be arranged in one row in the longitudinal direction.

In addition, two slider rails 303 may be inserted into a rail receiving groove 312 formed in the lower slider 31 in a pair. When the slider rail 303 is accommodated in the rail receiving groove 312, the second mass 24 on the support plate 21, the phase opposite to the phase of the excitation force generated by the rotational force of the drum It can swing in the horizontal direction. When the slider rail 303 is accommodated in the rail receiving groove 312, the second mass 24 may be prevented from swinging in the front-rear direction of the cabinet 11.

Although the slider receiving groove 312 is shown to accommodate two slider rails 303, it is not limited thereto, and it is understood that a structure in which three or more slider rails 303 are accommodated is also possible.

In addition, the lower slider 31 may have a rectangular shape having the same size as the upper slider 30.

In detail, the lower slider 31 may include a lower slider body 311 having the same shape as the upper slider body 301 and a length direction of the lower slider body 311 from an upper surface of the lower slider body 311. It may include an extended rail receiving groove 312 and a plurality of fastening protrusions 314 protruding from the bottom of the lower slider body 311.

Here, the protruding length of the slider rail 303 of the upper slider 30 may be formed to be equal to or slightly longer than the depression depth f of the rail receiving groove 312. In addition, the depression depth f of the rail accommodating groove 312 may be greater than a distance between the upper surface of the second mass 24 and the bottom surface of the top plate 12. In this case, even when the laundry treatment apparatus 10 is inverted or inclined during the movement of the laundry treatment apparatus 10, the phenomenon that the slide rail 303 is separated from the rail receiving groove 312 may be prevented. Can be.

In more detail, the plurality of fastening protrusions 314 may be formed in the same shape and the same number at the same formation position as the plurality of fastening protrusions 314 formed on the upper slider 30. Therefore, redundant description of the plurality of fastening protrusions 314 formed on the lower slider 31 is omitted. Of course, a plurality of slider fastening holes 218b for inserting the plurality of fastening protrusions 314 are formed in the support plate 21, specifically, the second forming part 217b of the support plate 21. do. The plurality of slider fastening holes 218b may be formed at a plurality of positions by forming a group corresponding to the number of the lower sliders 31.

In addition, the rail receiving groove 312 may have a width smaller than the width of the slider body 311 may be arranged in parallel with each other. In other words, the rail receiving groove 312 may be partitioned into a plurality of small rail receiving grooves by the partition wall 313.

In the present exemplary embodiment, the two rail receiving grooves 312 are disclosed to be arranged side by side in the width direction of the slider body 311, but three or more rail receiving grooves are not excluded. Of course, the partition wall 313 is not formed and does not exclude that a single rail receiving groove 312 is formed.

In addition, two or more slider rails 303 are received in each rail receiving groove 312, and at least two slider rails 303 contact the front and rear edges of the rail receiving groove 312. You can do that.

That is, the front rail of the at least two slider rails 303 accommodated in the rail receiving groove 312 is in contact with the front edge of the rail receiving groove 312, the rear rail is the rail receiving groove 312 Can be in contact with the rear edge of the. For example, when three slider rails are formed, two may contact the front and rear surfaces of the rail receiving groove 312, and the other may be disposed at the center of the rail receiving groove 312.

In this way, the front and rear surfaces and the bottom surfaces of the at least two slider rails 303 are in contact with the front and rear surfaces and the bottom surface of the rail receiving groove 312, so that the second mass 24 is in the horizontal direction (the length of the slider). Direction, the damping by the frictional force acts and the transient vibration is absorbed.

The frictional force generated by the slider 29 acts as an attenunation of the second mass 24. In addition, the damping of the second mass 24 serves as a variable for determining the vibration displacement of the transient vibration. In addition, the friction coefficient of the friction force determines the magnitude of the attenuation, and the greater the damping (or damping value), the better the absorber's ability to absorb excessive vibration.

Of course, the elastic damper 23 also has a damping to absorb not only the elasticity (or rigidity) but also the transient vibration, but it may affect the improvement of the transient vibration, but may be considerably smaller than the damping caused by the friction. Therefore, the elastic damper 23 may be referred to as a damper mainly affects to improve the normal vibration transmitted from the copper reducer 20 to the cabinet 11.

Moreover, the effect which prevents the said 2nd mass 24 from oscillating in the front-back direction (the front-back width direction of the said slider) of the said laundry processing apparatus 10 can also be acquired.

In addition, the upper slider 30 and the lower slider 31 may be formed of an engineering plastic made of polyoxymethylene (POM). In addition, since a noise may occur when the plastic of the same material moves while contacting, a lubricant such as grease may be applied to the rail receiving groove 312.

On the other hand, the length of the rail receiving groove 312 is formed longer than the length of the slider rail 303, so that the upper slider 30 can reciprocate in the left and right directions on the lower slider 31. This is because, if the upper slider 30 does not move left and right on the lower slider 31, the second mass 24 cannot vibrate in a phase opposite to that of the cabinet.

In detail, the value obtained by subtracting the length of the slider rail 303 from the left and right length of the rail receiving groove 312 is equal to or larger than the displacement of the second mass 24.

FIG. 23 is a top perspective view of a second elastic damper according to an embodiment of the present invention, and FIG. 24 is a bottom perspective view of the second elastic damper.

Referring to FIGS. 23 and 24, the copper reducer 20 according to the embodiment of the present invention includes a second elastic damper 27 which may be mounted on the side of the mass absorbing the transient vibration.

The second elastic damper 27 constituting the copper reducer 20 according to the embodiment of the present invention may be disposed at the left and right edges of the second mass 24.

In detail, when the second mass 24 swings in the horizontal direction, the left and right edges of the second mass 24 hit the second elastic damper 27. At this time, the second elastic damper 27 is elastically deformed to absorb the impact of the second mass 24.

In addition, two second elastic dampers 27 may be disposed at each of the left and right edges of the second mass 24, but the present invention is not limited thereto, and three or more second elastic dampers 27 may be disposed. . For example, it may be arranged at the rear end, the central part, and the front end of both side edges of the second mass 24, respectively.

The second elastic damper 27 may have a hexahedral shape including a front portion 271, a rear portion 274, a side portion 272, an upper surface portion 273, and a bottom surface portion 279. An inclined portion 275 may be formed or rounded at a corner portion where the front portion 271 and the upper surface portion 273 meet.

In addition, the round portion 276 or the inclined portion may be formed at the corner portion where the bottom portion 279 and the back portion 274 meet. When the inclined portion 275 is formed, when the horizontal force of the second mass 24 is applied to the front portion 271, the shape of the second elastic damper 27 rises while the top plate rises. Interference with (12) can be prevented.

In addition, when the round part 276 is formed, when the horizontal force of the second mass 24 is applied to the front part 271, the bottom edge of the rear end of the second elastic damper 27 protrudes. Interference with the side edge edges of the mass seating portion 241 can be prevented.

In addition, the second elastic damper 27 includes an elastic groove 277 recessed upward from the bottom portion 279, and a fastening arm protruding from the bottom portion 279 and fitted into the coupling slit 216. 278 may be further included.

In detail, the elastic groove 277 easily deforms the shape of the second elastic damper 27 when the second mass 24 presses the front portion of the second elastic damper 27 while swinging in the horizontal direction. It is formed to ensure good shock absorption. The elastic groove 277 may be defined as a shock absorbing groove, may be formed in a predetermined width in the left and right and front and rear directions, and may be recessed a predetermined depth upward.

The elastic groove 277 may be formed at a position adjacent to the front portion 271 rather than the rear portion 274 to facilitate shock absorption of the second mass 24. The elastic groove 277 may have a structure in which the elastic groove 277 is opened at the bottom of the second elastic damper 27 to be recessed upward, and is opened at the upper surface of the second elastic damper 27 to be recessed downward. Do. For example, it is noted that it is also possible to open at the inclined portion 275 and to be recessed to a predetermined depth downward.

In addition, the fastening arm 278 may include an extension end 278a extending from the bottom portion 279 by a predetermined length and a locking protrusion 278b extending from a side edge of an end of the extension end 278a. Can be.

That is, the end of the fastening arm 278 may be formed in an inverted T shape, but is not necessarily limited thereto. When the longitudinal cross-section of the fastening arm 278 is formed in an inverted T shape, the fastening slit 216 is formed in a T shape or an I shape, so that the fastening arm 278 can be inserted even more easily.

In detail, in order to couple the fastening arm 278 to the fastening slit 216, first, the second elastic damper 27 is obliquely inclined so that an end of the locking protrusion 278b is shorted to the fastening slit 216. To be in the department. In this case, the extension end 278a is positioned at the long side of the fastening slit 216. In this state, the locking projection 278b is pushed so as to be inserted into the short side of the fastening slit 216, and at the same time, the second elastic damper 27 is brought into a horizontal state. Move along the long side of the fastening slit 216. When the second elastic damper 27 is completely horizontal, the second elastic damper 27 is completely inserted into the fastening slit 216.

In addition, in order to prevent the second elastic damper 27 from swinging in the vertical direction while being coupled to the support plate 24, the length of the extension end 278a is equal to the thickness of the support plate 24. It may be of a corresponding length. In other words, the distance from the bottom portion 279 to the upper end of the locking protrusion 278b may be set equal to the thickness of the support plate 24.

The fastening arm 278 may be formed at a point closer to the rear portion 234 than the front portion 271 of the second elastic damper 27, but is not necessarily limited thereto.

25 is a top perspective view of the first elastic damper according to the embodiment of the present invention, FIG. 26 is a bottom perspective view of the first elastic damper, and FIG. 27 is a longitudinal cross-sectional view taken along the line 27-27 of FIG. 25.

25 to 27, the first elastic damper 26 according to the embodiment of the present invention may be mounted on the side of the mass body that absorbs the normal vibration.

In detail, the first elastic damper 26 may include a side support having the same shape as the second elastic damper and a bottom support extending horizontally from the side support.

In addition, two first elastic dampers 26 may be disposed at each of the left and right edges of the first mass body 23, but the present invention is not limited thereto, and three or more first elastic dampers 26 may be disposed. . For example, the rear end portion, the central portion, and the front end portions of both side edges of the first mass body 23 may be disposed.

The side support of the first elastic damper 26 may have the same shape as that of the second elastic damper 27. That is, the side support portion of the first elastic damper 26 has a hexahedral shape including a front portion 261, a back portion 264, a side portion 262, an upper surface portion 263, and a bottom surface portion 269. Can be. An inclined portion 265 may be formed or rounded at a corner portion where the front portion 261 and the upper surface portion 263 meet.

In addition, the first elastic damper 26 may further include an elastic groove 266 and a fastening arm 268. In detail, the elastic groove 266 may be recessed a predetermined depth downward from the upper surface portion 263, or may be recessed a predetermined depth upward from the bottom surface portion 269.

The fastening arm 268 may include an extension end 268a and a locking protrusion 268b. The fastening arm 268 may be inserted into the fastening slit 216 by fastening the fastening arm 278. It is the same as the method of inserting into the slit 216.

On the other hand, the bottom support portion, a portion for supporting the bottom edge of the first mass body 23, it may be composed of a horizontal portion (269a) and a vertical portion (269b).

In detail, the horizontal portion 269a may extend horizontally from the front portion 261, and the vertical portion 269b may extend downward from an end portion of the horizontal portion 269a. In addition, the horizontal portion 269a may be horizontally extended at a point spaced upward from a lower end of the front portion 261, and may be designed to be elastically deformable.

The first mass 23 is relatively larger in mass than the second mass 24 and operates at high speed rotation. That is, it vibrates at a high frequency in order to catch the normal vibration that occurs when the drum is maintained at the highest speed. In this case, not only the horizontal vibration but also the vertical vibration may occur in the first mass body 23. When the vertical vibration occurs, the left end and the right end of the first mass 23 may come into contact with the support plate 21 to generate noise. To prevent this, the bottom support may support the bottom left and right edges of the first mass 23.

Of course, when the level of the first mass 23 is maintained by the supporter 28, the second elastic damper 27 is a side surface of the first mass 23 instead of the first elastic damper 26. It may be arranged in. Ideally, the first mass body 23 is not in contact with the horizontal portion 269a in the course of swinging in the horizontal direction, which is advantageous in terms of lowering the friction damping. However, when the first mass 23 vibrates in a horizontal state, the horizontal portion 269a is maintained only when the first mass 23 is spaced apart from the horizontal portion 269a and the horizontal state of the first mass 23 is collapsed. By contacting, we can achieve both purposes.

Hereinafter, a description will be given of a method in which the copper reducer 20 effectively absorbs excessive vibration and normal vibration generated in the cabinet 11 to improve vibration.

Equation 1 below is a dimensionless response showing the behavior of the dynamic reducer 20 to the vibration generated when the drum having an eccentric load rotates.

,

Y is the dimensionless vibration displacement (or amplitude) of the mass,

r: driving speed ratio (or driving frequency ratio)

ω: rotational speed (or rotational frequency) of the drum

ω _a : natural frequency (or natural frequency) of the mass

ω _p : natural frequency (or natural frequency) of the laundry treatment apparatus

β: frequency ratio (or frequency ratio)

μ: mass ratio

m _a : mass of the mass

m _p : mass of laundry treatment unit

ζ: damping ratio

c _a : mass damping

The dimensionless response formula of the said copper reducer has mass ratio, frequency ratio, and damping ratio as variables. The mass ratio is strictly defined as the mass ratio of the mass body 22 to the mass of the laundry treatment apparatus 10. However, the mass ratio of the copper reducer 20 to the mass of the laundry treatment apparatus 10 is defined. It can also be seen by mass ratio.

This, because the elements other than the mass 22 of the components of the copper reducer 20 is fixed to the laundry treatment apparatus 10, it can be seen as part of the mass of the laundry treatment apparatus 10, the laundry treatment This is because it hardly affects the determination of the total mass of the device 10. This is because the upper slider 30 also has a mass that can be ignored relative to the mass of the mass 22. Therefore, the mass ratio may be interpreted as the mass ratio of the copper reducer 20.

The frequency ratio and the damping ratio may also be defined or interpreted as the frequency ratio of the dynamic reducer 20 and the damping ratio of the dynamic reducer 20 similarly to the mass ratio.

On the other hand, the shape of the response curve drawn by the response equation is determined by the mass ratio, the frequency ratio, and the damping ratio, and the vibration absorbing capacity of the dynamic reducer 20 is determined by these variables. That is, when the mass ratio, the frequency ratio, and the damping ratio, which are variables of the response equation, are selected appropriately, increasing the rotational speed ratio of the drum calculates the dimensionless amplitude of the dynamic reducer. And, the calculated dimensionless value can be seen as the vibration displacement of the cabinet (11).

Here, the mass ratio of the dynamic reducer 20 is a design variable that determines the absorption region for absorbing the transient vibration, and the frequency ratio (or frequency ratio) and the damping ratio are the design that determines the vibration displacement of the secondary transient vibration after the exhaustion. Variable. In detail, when the transient vibration absorbing mass body (second mass in the present invention) of the copper reducer 20 operates at the resonance point, the transient vibration is absorbed, and the two secondary transients are significantly smaller than the vibration displacement when the transient vibration occurs. Vibration occurs.

The distance between the two secondary transient vibrations is defined as a suction region or a suction width, and the size of the suction region may vary according to the mass ratio. In addition, the vibration displacement, that is, the peak point of the two secondary transient vibrations may be changed by adjusting the frequency ratio and the damping ratio.

For reference, in the response graph, the two second transient vibrations are represented by two peak points where the dimensionless amplitude value suddenly increases and decreases. The interval between the two peak points is interpreted as a suction region, and the interval between the two peak points is changed by adjusting the mass ratio.

On the other hand, the resonant frequency at which the excessive vibration occurs may vary depending on the size, mass, product deviation of the laundry treatment apparatus, the eccentricity of the laundry (load) is put into the drum. In this situation, in order for the copper reducer 20 to effectively absorb the excessive vibration of the laundry treatment apparatus 10 to improve the vibration, the suction region should be formed to be equal to or larger than the resonance frequency region.

Here, the suction region of the copper reducer 20, the rotational frequency at the time when the second mass 24 starts to move in a direction opposite to the excitation force generated by the acceleration and rotation of the drum, and the rotational speed of the drum As is increased, the vibration generated by the excitation force is reduced to be defined as the width between the rotation frequency at the time when the second mass 24 stops.

Here, the meaning of the point in time at which the mass starts to move may be defined as the point in time at which the mass vibrates in a phase different from that of the cabinet 11 or the support plate 21. In other words, the meaning of the point in time at which the mass stops may be defined as the point in time at which the mass starts to move in the same phase as the vibration phase of the cabinet 11 or the support plate 21.

In addition, a factor for determining the size of the transient vibration absorbing region of the copper reducer 20 is the mass ratio. That is, the larger the mass ratio, the wider the excessive vibration absorption region, and the smaller the mass ratio, the narrower the absorption region. In other words, it means that the larger the mass of the second mass 24 can absorb the transient vibration in a wide range.

The mass ratio may be increased in order to widen the suction area, but the internal space of the cabinet 11 in which the copper reducer 20 is mounted is limited. In detail, since the copper reducer 20 is mounted on the upper surface of the cabinet 11 and the copper reducer 20 is covered by the top plate 12, the planar area of the copper reducer 20 is increased. There is a limit that cannot increase the thickness indefinitely.

Theoretically, if the mass of the copper reducer 20, specifically, the mass of the mass 21 and the total mass of the laundry treatment apparatus 10 to which the copper reducer 20 is mounted, is equal to the transient vibration, Absorb perfectly.

However, if the mass of the mass 21 is excessively large, the load of the laundry treatment apparatus 10 is too large, which makes it difficult to move and install, and sagging due to the weight of the second mass 21 may occur. Above all, there is a limit in increasing the load (or mass) of the second mass 21 due to the limitation of the installation space inside the cabinet 11.

In addition, when only the second mass 21 is installed, transient vibration may be improved, but a problem in which normal vibration cannot be absorbed may occur. That is, there is a problem that it is not possible to absorb both transient vibration and normal vibration in one mass.

FIG. 28 is a graph showing vibration displacement of a laundry treatment apparatus equipped with a copper reducer including only a mass for transient vibration absorption.

The horizontal axis of the graph represents the rotational speed (rpm) of the drum, and the vertical axis represents the vibration displacement of the cabinet. The rotational speed can be seen in the same concept as the rotational frequency.

Referring to FIG. 28, a graph A is a vibration displacement graph of a cabinet measured by a laundry treatment apparatus in which the copper reducer 20 is not mounted, and a graph B is a laundry treatment apparatus equipped with a mass for absorbing excessive vibration having a predetermined mass ratio. Vibration displacement graph of the cabinet being measured at.

First, let's look at the case where the copper reducer is not installed.

A drum loaded with laundry for rinsing or dehydration starts to rotate, and a horizontal excitation force is generated by the rotation of the eccentric laundry introduced into the drum as the rotation speed increases. The vibration force also increases the horizontal vibration displacement of the cabinet.

When the rotational speed of the drum reaches a resonance frequency, the cabinet vibrates excessively by resonance. On the graph, the resonance point at which the transient vibration occurs is identified as a section between 800 rpm and 1000 rpm.

In addition, the vibration gradually decreases when the drum's rotational speed exceeds the resonance frequency. In addition, in the section where the drum is maintained at the maximum speed, the cabinet is subjected to the normal vibration in which the vibration displacement value hardly changes.

On the other hand, when the copper reducer is mounted, the vibration displacement of the cabinet 11 also increases as the rotational speed of the drum increases. In the low speed section in which the dynamic reducer is not started, the behavior of the vibration displacement graph is not significantly different from the case where the dynamic reducer is not mounted.

However, when the drum's rotational frequency (or rotational speed) falls within the dynamic range of the oscillator, i.e., the mass starts, the mass starts to move. Then, the vibration displacement of the increased cabinet is sharply decreased, and the vibration displacement of the cabinet, which is suddenly decreased as the rotation speed of the drum increases, gradually increases again. That is, it can be seen that the transient vibration generated when the copper reducer is not mounted is absorbed by the copper reducer.

Then, the rotational speed of the drum continues to increase, and the vibration displacement of the cabinet increases until the vibration of the mass stops, and the mass stops when the rotational speed of the drum leaves the suction region of the copper reducer.

In detail, when the drum exceeds the resonance frequency, vibration caused by the excitation force is weakened, and vibration displacement of the cabinet is also reduced. Therefore, when the rotational speed of the drum is out of the transient vibration absorption region of the copper reducer 20, the vibration displacement of the cabinet decreases and is maintained at the displacement in the normal vibration.

Here, in the graph B, it can be seen that two inflection points (a, b) having a vibration displacement less than the vibration displacement in the transient vibration is formed while the transient vibration is absorbed by the copper reducer 20. The vibrations at the two inflection points may be defined as secondary transient vibrations. In addition, the two inflection points a and b correspond to two peak points appearing in the response curve. The distance W between two inflection points may be defined as the suction region or the suction width.

In detail, the two secondary transient vibrations appear at the initial and end points of the suction, respectively. The front secondary transient vibration is a vibration that appears because the mass absorbs the vibration that has increased with the start of the motion. The secondary transient vibration at the rear side is a vibration that occurs because the cabinet behaves under the same conditions as when the dynamic reducer 20 is not mounted while the mass stops behaving.

In addition, when the suction region is widened through the adjustment of the mass ratio, the vibration displacement in the secondary transient vibration can be further reduced, and the time point at which the front secondary transient vibration occurs can be advanced to the low speed section. Then, there is an advantage in that the stability of the washing machine is improved as compared with the case in which excessive vibration occurs in the high speed section.

In addition, by adjusting the frequency ratio and the damping ratio, it is possible to control the vibration displacement in the rear secondary transient vibration significantly lower than the vibration displacement in the front secondary transient vibration.

Here, two secondary transient vibrations occur because the amount of vibration absorption is greatest at the resonance point of the drum. That is, since the mass 21 is designed to vibrate the largest in the direction opposite to the vibration direction generated by the excitation force at the resonance point where the transient vibration occurs, so as to absorb the excessive vibration as much as possible, both ends of the suction region It is natural that the second transient vibration occurs at.

29 is a graph showing vibration displacement of the laundry treatment apparatus equipped with the copper reducer according to the embodiment of the present invention.

In detail, the graph D is a graph showing the vibration displacement of the cabinet according to the rotational speed of the drum in a state where the copper reducer is not mounted, and may correspond to the graph A of FIG. 28.

Graph E is a graph showing the vibration displacement of the cabinet which appears when only the mass corresponding to the first mass, that is, the mass absorbing normal vibration, is mounted.

And, the graph F is a graph showing the vibration displacement of the cabinet shown when the copper reducer 20, that is, the mass absorbing normal vibration and the mass absorbing transient vibration, according to an embodiment of the present invention are all installed separately. to be.

In order to design the vibration pattern of the cabinet as shown in the graph E, first, only the first mass 23 is mounted to determine the vibration displacement of the cabinet. That is, the mass ratio, the frequency ratio, and the damping ratio of the first mass in consideration of the size of the given support plate 21, the distance between the support plate 21 and the top plate 12, and the desired normal vibration reduction amount, And so on.

The vibration displacement of the cabinet 11 then moves from graph D to graph E, as shown. Looking at the graph E, it can be seen that the normal vibration displacement is reduced by about 200 micrometers from t1 to t2 by the first mass. At this time, by the mounting of the first mass, although not large, the transient vibration displacement is also reduced by about 100 micrometers from h1 to h2, and at the same time it can be seen that the location of the transient vibration is moved to the low speed section. Since the first mass has a main target of absorbing the normal vibration rather than the transient vibration, it can be seen that the first mass does not significantly affect the transient vibration reduction.

In this state, the first mass 23 is included as a part of the mass of the laundry treatment apparatus, and the optimum mass is inputted in the response equation while appropriately changing the mass ratio, the frequency ratio and the damping ratio of the second mass 24. This can be determined. And when the vibration displacement of the cabinet 11 is measured in the state which also attached the said 2nd mass 24, the graph E will move to the form of the graph F. FIG.

In other words, it can be seen that the vibration pattern of the cabinet is changed from the graph D when the copper reducer 20 is mounted from the graph D when the copper reducer 20 according to the embodiment of the present invention is not mounted.

Looking at the graph F, by the operation of the second mass 24, the transient vibration that would have occurred between about 800rpm to 900rpm is absorbed, resulting in two secondary transient vibrations with less vibration displacement. And, the peak point of the rear secondary transient vibration among the two secondary transient vibrations can be further reduced by appropriate adjustment of the mass ratio, the frequency ratio, and the damping ratio.

In addition, it can be seen that the normal vibration is reduced from t1 to t3 by the first mass body 23. And since the normal vibration was reduced from t2 to t3, it can be seen that the second mass 24 also contributed to absorbing the normal vibration to some extent, although it was not large.

On the other hand, since the size of the support plate 21 on which the first mass 23 and the second mass 24 is seated is limited, the overall size of the mass receiving portion 214 formed on the support plate 21 is limited. The mass ratio of the first mass 23 and the second mass 24 should be appropriately adjusted from the maximum mass of the corresponding mass. Since the mass of the first mass 23 for absorbing the normal vibration must be greater than the mass of the second mass 24 for absorbing the transient vibration, only the second mass 24 itself can be covered. There is a limit to increasing the possible transient vibration damping width.

In order to overcome this, the behavior section of the second mass 24 and the behavior section of the first mass 23 are partially overlapped, so that the first mass 23 contributes to increasing the transient vibration absorption width. You can do that. As a result, it is possible to obtain an effect of maximizing the vibration improving efficiency of the cabinet 11.

Referring back to the graph 29, when the drum starts to rotate and is gradually accelerated, the vibration of the cabinet 11 is gradually increased by the excitation force generated by the eccentric load put into the drum.

Then, if the rotational speed of the drum increases to some extent (about 800 rpm in the figure), the left-right behavior (or vibration) of the second mass 24 begins. At the resonance point where the transient vibration occurs, the second mass 24 vibrates greatly to absorb the transient vibration. Then, the front secondary transient vibration (peak point k1) occurs, and the vibration displacement of the cabinet 11 decreases and then increases again.

Here, the movement of the first mass 23 is started at the point where the movement of the second mass 24 ends, that is, approximately 950 rpm in the drawing. In addition, the second mass 24 stops at an interval of approximately 1050 rpm to 1100 rpm, after which only the first mass 23 behaves. Then, at the point where the rear secondary transient vibration occurs, the first mass 23 is not large, but contributes to absorbing a certain level of transient vibration. As a result, the rear secondary vibration (peak point k2) is extinguished to the extent that it hardly appears, and there is an advantage that the transient vibration region is also widened.

In the drawing, W1 denotes a transient vibration-absorbing region (section in which the second mass moves), W2 denotes a normal vibration-absorbing region (section in which the first mass moves), and W3 denotes an overlapping section (first and second mass bodies). Section together to exercise).

In order to obtain the above-described results, that is, the cabinet vibration pattern of the graph F, the design condition of the dynamic reducer 20 is set using the response equation shown in Equation 1, and the dynamic reducer 20 is set to the set design condition. As a result of fabrication and direct vibration measurement, the following design conditions were obtained.

First, looking at the design variable region for improving the normal vibration, the mass ratio of the first mass 23 is 4% ~ 10%, the frequency ratio (or frequency ratio) is 0.8 ~ 1.5, the damping ratio is 0% ~ 20% Can be set.

When the mass ratio of the first mass 23 is less than 4%, since the absorption width that the first mass 23 can cover is too narrow, there is no overlapping region with the second mass 22 and the second mass Problems can arise where (22) does not help to absorb transient vibrations. In addition, there may be a problem that can not absorb the normal vibration occurring in the region outside the coverable absorption width.

On the other hand, the maximum value of the mass ratio of the first mass 23 is 10% due to the internal spatial constraints of the laundry treatment apparatus 10 in which the copper reducer 20 is mounted and the total weight limitation of the laundry treatment apparatus 10. It is preferable to set to.

In addition, since the normal vibration generated in the laundry treatment apparatus 10 occurs a lot in the range of approximately 900 rpm to 1300 rpm, the first mass 23 should be designed to absorb the normal vibration generated in the region. However, when the frequency ratio of the first mass 23 is less than 0.8 or more than 1.5, the target suction region may be out of the section where the normal vibration occurs, which may result in the failure to absorb the normal vibration.

In addition, looking at the design variable region for improving the transient vibration, the mass ratio of the second mass 24 may be set to 2% to 5%, the frequency ratio of 0.5 to 1, the damping ratio of 20% to 50%. Similarly to the reason for setting the mass ratio of the first mass 23, the mass ratio of the second mass 24 is less than 2%, and the absorption width is excessively narrowed, so that a region that cannot absorb excessive vibration may occur. Then, the maximum mass ratio was set not to exceed 5% due to the space constraints inside the laundry treatment apparatus and the weight limitation of the laundry treatment apparatus.

In addition, the mass ratio of the second mass 24 to the first mass 23 may be set to 40% to 60%. In addition, the space inside the cabinet of the laundry treatment apparatus 10 to which the copper reducer 20 is mounted is limited, and in particular, the area of the support plate 21, the support plate 21 and the top plate 12 are limited. It is important to appropriately set the mass ratio between the first mass 23 and the second mass 24 in a state where the interval therebetween is determined.

If the mass ratio of the second mass 24 to the first mass 23 is set to less than 40%, the normal speed of absorbing vibration is improved, but a rotational speed range that cannot absorb excessive vibration is generated. On the contrary, when the mass ratio of the second mass 24 to the first mass 23 exceeds 60%, the transient vibration absorption capacity is improved while the first mass is reduced due to the mass reduction of the first mass 23. The natural frequency of the mass body 23 becomes high. As a result, the frequency ratio of the first mass body 23 is increased, so that the rotational speed region in which the normal vibration absorption region does not absorb the normal vibration while moving to the high frequency region, that is, the high speed region, is generated. In addition, when the normal vibration absorbing region moves to a high speed section, a problem arises in that the overlapping region where the motion section of the second mass 24 overlaps with the motion section of the first mass body 23 is eliminated.

In addition, the vibration ratio and the damping ratio of the first damper 23 and the second damper 24 are the elastic modulus and damping of the elastic damper 25, the elastic modulus and damping of the supporter 28 and the slider 29. It can be implemented by the complex design of.

For example, the hardness of the first elastic damper 26 is preferably set within the range of 30 to 60 under the conditions of manufacturing the shape as shown. In addition, the hardness of the second elastic damper 27 is preferably set within the range of 20 to 50 under the condition of being manufactured in the shape as shown.

In addition, the supporter 28 preferably applies a roller or ball bearing to minimize frictional force, and the slider 29 preferably generates an appropriate kinetic frictional force to cover the set excessive vibration absorption area.

Claims

cabinet;

A drum housed in the cabinet;

A tub for receiving the drum; And

Includes; a copper reducer provided to absorb the vibration of the cabinet,

The copper reducer,

A support plate coupled to the cabinet; And

A mass body movably placed on the support plate to absorb vibrations transmitted to the cabinet,

And a partition wall for partitioning an upper surface of the supporting plate on which the mass is placed into a first receiving portion and a second receiving portion, protruding from an upper surface of the supporting plate.
The method of claim 1,

The mass is

A first mass placed on the first receiving portion,

A second mass placed on the second receptacle,

The mass of a said 1st mass is larger than the mass of a said 2nd mass, The laundry processing apparatus characterized by the above-mentioned.
The method of claim 2,

The support plate,

A plate body placed on an upper surface of the cabinet,

An outer wall protruding upward from an upper surface of the plate body and surrounding the edge of the plate body;

And the first and second receiving parts are formed inside the outer wall.
The method of claim 3, wherein

The partition wall extends in the horizontal direction of the plate body, wherein the first receiving portion is defined in front of the partition wall, the second receiving portion is laundry treatment apparatus characterized in that the rear of the partition wall.
The method of claim 3, wherein

The front and rear width of the first accommodating portion is larger than the front and rear width of the second accommodating portion.
The method of claim 3, wherein

The plate body, the laundry treatment apparatus characterized in that one or a plurality of forming parts for strength reinforcement is formed.
The method of claim 3, wherein

Laundry treatment apparatus, characterized in that a plurality of drainage holes are formed in the plate body.
The method of claim 3, wherein

Laundry treatment apparatus, characterized in that the left and right edge of the plate body extends a plurality of cabinet coupling portion.
The method of claim 3, wherein

A supporter provided between the first mass and the support plate to support the first mass;

And a slider provided between the second mass and the support plate to enable sliding movement of the second mass.
The method of claim 9,

Laundry plate processing apparatus, characterized in that the supporter mounting portion to which the supporter is mounted is formed in the plate body portion defining the first housing.
The method of claim 9,

The plate body portion defining the second accommodation portion is a laundry treatment device characterized in that the slider fastening hole is mounted is formed.
The method of claim 2,

A plurality of elastic dampers fixed to the support plate and supporting left and right sides of the first and second masses,

Laundry treatment apparatuses, characterized in that fastening slits are formed on the left and right edges of the first and second receptacles to which the plurality of elastic dampers are mounted.
The method of claim 12,

Each of the plurality of fastening slits, the laundry treatment apparatus, characterized in that the incision in the T-shape or I-shape.
The method of claim 1,

Laundry treatment apparatus, characterized in that the first mode resonance frequency of the support plate is in the range of 20Hz ~ 30Hz.