JP2006230591A - Drum type washing machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a drum type washing machine which can obtain the accurate damping force corresponding to the amplitude regardless of the drum rotation frequency and has a suspension to be capable of controlling the inclination of a rod relative to a cylinder. <P>SOLUTION: On the occasion of a reciprocating motion of the rod 23, the rod 23 is made to slide on a friction member 21 and is supported by two points of a shaft bearing 17 and a resinous guide 28 disposed at both upper and lower sides across the friction member 21. Thereby, the damping force corresponding to the amplitude can be obtained by the slide between the friction member 21 and the rod 23 and the rod 23 becomes not easy to be inclined relative to the cylinder 15 since the rod 23 is supported by two points. Moreover, by letting one of both the sides across the friction member 21 be the guide 28 which moves with the rod 23 as one body, a cheaper material can be used for the guide 28 than the shaft bearing 17 so that the construction becomes cheaper as compared to the case to let both the sides be the shaft bearings 17. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a drum-type washing machine having a structure in which a water tank containing a drum is supported by vibration-proofing by a suspension.

A conventional drum-type washing machine is generally configured such that a horizontal axis drum for housing clothes is rotatably provided in a water tank for storing washing water. In this configuration, the drum is rotationally driven by a motor via a rotating shaft supported by a bearing, and the water tank that accommodates the drum is subject to vibrations generated by washing, dehydration, drying processes, etc. It is supported by multiple suspensions so that it is not transmitted directly to the base plate. As such a suspension, two types of oil damper type and friction damper type are mainly known.
Hereinafter, simple configurations and characteristics of the oil damper type suspension and the friction damper type suspension will be described. First, FIG. 9 shows an example of an oil damper type suspension.

The suspension 102 includes an oil damper 100 and a coil spring (spring) 101. In the suspension 102, the cylinder 103 constituting the oil damper 100 has one end 103a fixed to the bottom plate 104 of a water tank (not shown), and vibrates in the vertical direction together with the water tank. The cylinder 103 is filled with oil 105. An end 107a of a rod 107 (generally a member called a piston rod) is fixed to the base plate 106 of the outer box of the drum type washing machine so as to coincide with the cylinder 103 in the axial direction. It is fixed to.
The other end portion 107b of the rod 107 is inserted into the cylinder 103 in a liquid-tight manner, and has an outer diameter substantially the same as the inner diameter of the cylinder 103 and a plurality of holes 108a formed in the axial direction at the tip end portion. The disc member 108 (generally called a piston valve) is fixed. Each of the cylinder 103 and the rod 107 is provided with flanges (so-called spring receiving portions) 109 and 110 so as to face each other, and the coil spring 101 extends and contracts between the flanges 109 and 110. Arranged freely. Thus, the cylinder 103 and the rod 107, that is, the bottom plate 104 and the base plate 106 are configured to be separated from each other by a fixed distance in normal times.

  In the suspension 102 having such a configuration, when the water tank vibrates in the vertical direction, the cylinder 103 (of the oil damper 100) also reciprocates in the axial direction (vibrates in the vertical direction) with the expansion and contraction of the coil spring 101. As a result, the rod 107 relatively reciprocates in the cylinder 103. Accordingly, the disk member 108 reciprocates in the axial direction in the oil 105 filled in the cylinder 103, so that the oil 105 passes through the plurality of holes 108a formed in the disk member 108. become. Due to the viscosity of the oil 105 at this time, a damping force is generated in the oil damper 100 to attenuate the amplitude of the water tank.

Here, the damping force D generated as described above is generally expressed by the following equation (A).
Damping force D = Inlet loss + Friction loss + Dynamic pressure resistance (A)
The inlet loss is a pressure loss generated when the oil 105 flows into the hole 108a of the disc member 108, and the friction loss is a pipe friction when the oil 105 passes through the hole 108a. It is the pressure loss by. The dynamic pressure resistance is a pressure loss due to the fact that the dynamic pressure of the oil 105 does not recover at the back surface of the disk member 108.

  The inlet loss, friction loss, and dynamic pressure resistance that generate the damping force D of the oil damper 100 are generally approximately proportional to the square of the relative speed between the cylinder 103 and the disk member 108. Furthermore, when the amplitude of the water tank is constant, the relative speed is proportional to the drum rotation frequency. Therefore, the relationship between the drum rotation frequency and the damping force D is a quadratic curve as shown in FIG. That is, the damping force of the oil damper type suspension 102 has a characteristic that it increases in proportion to the drum rotation frequency.

On the other hand, as an example of a friction damper type suspension (see, for example, Patent Document 1), although not shown, a cylindrical cylinder, a rod-shaped rod that reciprocates in the cylinder, and the movement of the rod 2. Description of the Related Art It is known to have a cylindrical friction member that slides on the inner peripheral surface of the cylinder and supports the rod with respect to the cylinder. This suspension obtains a damping force (Coulomb friction force) E as shown by the following equation by sliding between the cylinder and the friction member.
Damping force E = μN (μ: friction coefficient, N is vertical drag) ... (B)
As can be seen from this equation, the damping force of the friction damper type suspension has a characteristic that it does not depend on the drum rotation frequency.
JP-A-6-154479

By the way, the vibration of a general drum-type washing machine shows a steady behavior after passing through a plurality of resonances from the start of dehydration, and its amplitude is determined by the eccentric amount ε of the drum rotation center and the drum center of gravity. In other words, the drum-type washing machine has a low drum rotation frequency range where resonance of the water tub exists, and when the eccentricity ε is large due to the displacement of the laundry, the amplitude increases, and in a high drum rotation frequency range after passing through the resonance. In addition, when the deviation of the laundry is eliminated and the amount of eccentricity ε is small, the amplitude is small.
For this reason, as described above, the oil damper type suspension 102 having the characteristic that the damping force increases in proportion to the drum rotation frequency is completely opposite to the characteristic of the drum type washing machine, It is not suitable for use.
On the other hand, the friction damper type suspension is suitable for use in view of the characteristics of the drum type washing machine because the damping force does not depend on the drum rotation frequency. However, the general friction damper as described above has a structure in which the circumferential load generated by the relative reciprocation of the rod with respect to the cylinder is supported only by the outer peripheral surface of the friction member. For this reason, there is a problem that the friction member is easily worn and the durability is low, and the rod is easily inclined with respect to the cylinder.

  The present invention has been made in view of the above circumstances, and an object thereof is to obtain an accurate damping force according to the amplitude regardless of the drum rotation frequency, and in addition, it is possible to suppress the inclination of the rod with respect to the cylinder. Another object of the present invention is to provide a drum type washing machine having a suspension.

In order to achieve the above object, the present invention provides a drum-type washing machine having a suspension for supporting a vibration-damping water tank containing a drum.
The suspension is
A tubular member;
A bearing which is supported and fixed inside the cylindrical member and has a shaft insertion hole in the center,
A rod inserted into the shaft insertion hole and supported so as to be capable of reciprocating relative to the bearing;
A cylindrical friction member that is fitted to the outer periphery of the rod inside the cylindrical member and attenuates the amplitude of the water tank by a frictional force with the rod generated by the relative movement of the rod;
A spring disposed between the cylindrical member and the rod;
The cylindrical member is attached to the rod so as to move integrally with the rod, with the friction member being sandwiched between the outer peripheral surface and the inner peripheral surface of the cylindrical member. It is characterized by having a guide which contacts (Invention of Claim 1).

  According to such a configuration, first, the damping force depends on the frictional force between the rod and the friction member, so that the water tank vibration can always be accurately absorbed regardless of the drum rotation frequency. In addition to the friction member, the rod is supported not only by the friction member but also by bearings and guides existing on both sides of the friction member, so that the rod is difficult to tilt with respect to the cylinder.

  As described above, according to the present invention, it is possible to obtain an excellent damping effect that an accurate damping force corresponding to the amplitude can be obtained regardless of the drum rotation frequency and that the tilt of the rod with respect to the cylinder can be suppressed. be able to. In addition, the rod is a member that is supported on both sides of the friction member, and one is a bearing fixed to the cylinder, and the other is a guide that moves in the cylinder together with the rod. Thus, it is possible to use a material other than the special material as described above, and it is possible to use a material cheaper than the bearing. For this reason, compared with the case where a bearing is arrange | positioned on both sides of a friction member, it comes to be able to be cheap.

<First embodiment>
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.
First, FIG. 2 shows a longitudinal sectional view of the entire drum type washing machine. In FIG. 2, a laundry doorway 2 is formed at the center of the front portion (left side in FIG. 2) of the outer box 1 forming the outer shell of the drum type washing machine, and the laundry doorway 2 is opened and closed. A door 3 is provided. An operation panel 4 is provided at the upper part of the front portion of the outer box 1, and this operation panel 4 is used by the user for various operations related to the operation of the drum type washing machine. A number of operation switches (not shown) such as a start switch and various selection switches are provided.

  A water tank 5 is disposed inside the outer box 1. This aquarium 5 has a cylindrical drum shape, and is arranged in an oblique horizontal axis in which the axial direction is front and rear (left and right in FIG. 2) and forwardly inclined (upward to the left in FIG. 2). In addition, the anti-vibration support is provided by a pair of left and right suspensions 6 (only one is shown). The specific configuration of the suspension 6 will be described later.

  Inside the water tub 5, a drum 7 serving as a tub for storing laundry is disposed. The drum 7 also has a cylindrical drum shape, and is arranged coaxially with the water tank 5 (axial direction is front and rear, and the slanted horizontal axis is an upwardly inclined shape). The drum 7 also functions as a washing tub, a dewatering tub, and a drying tub. For this reason, a small hole 8 (only a part of which is shown) is a water hole and a vent hole in almost the entire body. Many are formed. Both the water tub 5 and the drum 7 have openings 9 and 10 for putting in and out the laundry on the front surface portion, and the opening 9 of the water tub 5 is the laundry entrance 2 of the outer box 1 by the bellows 11. The opening 10 of the drum 7 faces the opening 9 of the water tank 5.

  A motor 12 that rotationally drives the drum 7 is disposed on the back surface of the water tank 5. In this case, the motor 12 is an outer rotor type DC brushless motor, and the drum 7 is directly rotated by the motor 12. Further, a drain hose 14 is connected to the lower surface of the water tank 5 via a drain valve 13 so that washing water in the water tank 5 and thus in the drum 7 is discharged through these.

Next, a specific configuration of the suspension 6 described above will be described with reference to FIG.
As shown in FIG. 1, the suspension 6 has a cylinder 15 corresponding to a cylindrical member. One end (upper end in FIG. 1) of the cylinder 15 is fixed to the bottom plate 5a of the water tank 5 (only part of which is shown in FIG. 2) with a nut 15b via a vibration isolator 15a and the like. It is designed to vibrate vertically. On the other hand, at the other end of the cylinder 15 (the lower end in FIG. 1), a cylinder-side spring receiving portion 16 is provided on the outer periphery thereof, and a bearing 17 is disposed inside the other end. The bearing 17 has a shaft insertion hole 17a at the center, and is composed of, for example, a sintered oil-impregnated metal (so-called bearing alloy) and a metal press-fitting metal (so-called back metal). The bearing 17 is positioned in the cylinder 15 by the lower side (the lower side in FIG. 1) of the bearing 17 being in contact with the caulking portion 18 of the cylinder 15.

A pair of cylindrical cases 19 and 20 are disposed above the bearing 17 so as to be fitted to the inner peripheral surface of the cylinder 15. The tip portions of the cases 19 and 20 facing each other are in contact with each other in the vertical direction so that there is no gap. Further, on the inner peripheral surfaces of the cases 19 and 20, a fitting surface 22 for fitting with a friction member 21 described later and an oil reservoir for holding a lubricant in cooperation with a rod 23 described later. 24 are formed.
Of the cases 19 and 20, the upper case 19 (upper side in FIG. 1) has an inclined surface 25 on the upper side (upper side in FIG. 1) of the case 19 abutting on the constricted portion 26 of the cylinder 15. Positioned in the cylinder 15, the lower case 20 (lower side in FIG. 1) is positioned by the lower surface of the case 20 coming into contact with the upper surface of the bearing 17.

One end portion (lower end portion in FIG. 1) of the rod 23 that constitutes the suspension 6 together with the cylinder 15 is fixed to the base plate 1a of the drum-type washing machine (only a part is shown in FIG. 2). 15 is fixed with a nut 23b through a vibration isolator 23a or the like (see FIG. 2) so as to coincide with the shaft 15 in the axial direction. The other end portion (the upper end portion in FIG. 1) of the rod 23 is inserted into the shaft insertion hole 17a of the bearing 17 and reaches the cylinder 15, and is configured to be able to reciprocate relative to the bearing 17. .
On the outer periphery of the rod 23, the friction member 21 described above that can slide with the rod 23 is fitted at a position located between the pair of cases 19 and 20. The friction member 21 is in a substantially immobile state (non-movable state in the vertical direction) by the cases 19 and 20, and the rod 23 moves relative to the friction member 21 to generate a frictional force. It has become. The friction member 21 is made of, for example, synthetic rubber, and has a cylindrical shape as a whole. In the friction member 21, a contact surface 27 that forms an inclined surface is formed on the outer peripheral portions on both sides in the axial direction, and the contact surface 27 is the fitting surface 22 on which the cases 19 and 20 are formed. It comes to contact with.

A lubricant for preventing wear is applied to a portion of the friction member 21 that slides with the rod 23, that is, an inner peripheral surface, and an oil reservoir 24 (coordinated with the rod 23) formed in the cases 19 and 20 described above. A certain amount of lubricating oil is also stored. The lubricant preferably has a particle size of about several μm, for example, containing molybdenum (MnO ₂ ). The reason for this is that the inner circumference of the friction member 21 and the outer circumference of the rod 23 are almost free from each other when viewed macroscopically, but there are slight irregularities on the sliding surface when viewed microscopically. is there. That is, since the particle diameter of the molybdenum is extremely small, it enters into the concave and convex voids of the sliding surface and exhibits an effect of preventing wear.

A disc-shaped guide 28 is fixed to the rod 23 on the side opposite to the bearing 17 with the friction member 21 interposed therebetween, that is, on the tip of the rod 23. The guide 28 is fixed to the rod 23 by a swaging process (a process in which the tip of the rod 23 is inserted into the guide 28 and then the tip of the rod 23 is crushed to be integrated with the guide 28 and the rod 23). The material is made of hard resin, for example. As a result, the guide 28 and the rod 23 move integrally. At this time, the outer peripheral surface of the guide 28 is slidable (contactable) with the inner peripheral surface of the cylinder 15. Although not shown, the guide 28 has a plurality of holes in its axial direction.
On the outer periphery of the rod 23 in the vicinity of the one end (the lower end in FIG. 1), a rod-side spring receiving portion 29 is provided so as to face the cylinder-side spring receiving portion 16 in the axial direction. A coiled spring 30 extends and contracts between the rod-side spring receiving portion 29 and the cylinder-side spring receiving portion 16 (between the cylinder 15 and the rod 23) and on the outer periphery of the cylinder 15 and the rod 23. Arranged freely.
In the drum type washing machine provided with the suspension 6 configured as described above, when the water tank 5 vibrates in the vertical direction as the operation starts, the cylinder 15 also expands and contracts the spring 30 in conjunction with this. Accordingly, the rod 23 reciprocates in the axial direction (vibrates in the vertical direction), and the rod 23 relatively reciprocates in the cylinder 15. Thereby, a damping force is generated by friction between the rod 23 and the friction member 21.

  Here, the relationship between the displacement of the rod 23 and the damping force in the suspension 6 at this time will be described with reference to FIG. In addition, the amplitude of the rod 23, the period of vibration, and the like are not constant depending on the amount of laundry and the like, and accordingly, the magnitude and direction of the damping force constantly change. Therefore, for convenience of explanation, FIG. 3 illustrates only the damping force generated by sliding between the friction member 21 and the rod 23, and further assumes that the amplitude and vibration period of the rod 23 are always constant.

First, it is assumed that the rod 23 starts moving forward (moving upward in FIG. 1) relative to the cylinder 15, for example, while being supported by the bearing 17 and the guide 28 from the normal state. Accordingly, the inner circumferential surface of the friction member 21 slides with the outer circumferential surface of the rod 23 that moves forward, and the rod 23 receives a Coulomb friction force (friction force) from the friction member 21, thereby generating a damping force. . At this time, the friction member 21 receives a force that is dragged upward due to friction with the rod 23, whereby the contact surface 27 of the friction member 21 comes into strong contact with the fitting surface 22 of the case 19. Thus, the upper part of the friction member 21 is recessed in the radial direction.
As a result, the rod 23 receives a stronger Coulomb frictional force from the friction member 21 and abruptly a damping force (hereinafter referred to as a forward damping direction is referred to as a positive damping force). , A region above the horizontal axis) occurs (point A in FIG. 3). When the forward movement of the rod 23 further proceeds, the positive damping force continues to increase, but eventually the force with which the contact surface 27 of the friction member 21 contacts the fitting surface 22 of the case 19 is constant (the rod 23 Therefore, the positive damping force settles at a constant value (point B in FIG. 3), and the constant value decays until the forward movement of the rod 23 stops. Hold power.

When the forward movement of the rod 23 stops with the passage of time, the positive damping force does not rapidly decrease at that point (point C in FIG. 3), and then the rod 23 relatively moves backward (in FIG. When the movement starts to move, the friction member 21 and the rod 23 slide in a direction opposite to the above direction, and suddenly a negative damping force (hereinafter referred to as a positive damping) due to the same action as the positive damping force. A damping force in the direction opposite to the force is referred to as a negative damping force.) Occurs (point D in FIG. 3).
If the return movement of the rod 23 further progresses, the negative damping force continues to increase, but eventually settles to a constant value (point E in FIG. 3) as in the case of the positive damping force until the backward movement of the rod 23 stops. During this period, the constant damping force is maintained. Then, when the backward movement of the rod 23 is stopped, the negative damping force is not rapidly reduced at that time (point F in FIG. 3). Thereafter, the rod 23 returns to the point A and repeats the same action or the opposite action depending on the behavior of the water tank 5.

According to the present embodiment as described above, the suspension 6 is configured such that the damping force is caused by the friction force between the rod 23 and the friction member 21. For this reason, the damping force obtained from the suspension 6 can be caused not by the rotation frequency of the drum 7 but by the amplitude, so that an appropriate damping force is always generated for the water tank 5 (drum 7). Can do. Further, since the lubricant is applied to the friction member 21, it is difficult to cause excessive friction with the rod 23, thereby obtaining a stable and smooth damping force and preventing the friction member 21 from being worn. it can.
Further, the rod 23 is supported by the bearing 17 and the guide 28 that exist on both sides of the friction member 21 in addition to the friction member 21. For this reason, since the load of the amplitude of the water tank 5 receives the said load in the bearing 17 (inner peripheral surface) and the guide 28 (the guide 28 is the outer peripheral surface), the sliding area is large and surface pressure is inevitably increased. And the rod 23 is difficult to incline with respect to the cylinder 15, so that the characteristics can be stabilized and the suspension 6 can be further durable.

Further, the rod 23 is a member that supports the friction member 21 on both sides, and one is a bearing 17 fixed to the cylinder 15, and the other is a guide 28 that moves in the cylinder 15 together with the rod 23. Therefore, the guide 28 can be made of a material other than a special material such as the bearing 17, and can be used with a material cheaper than the bearing 17. For this reason, compared with the case where the bearing 17 is arrange | positioned at the both sides of the friction member 21, it can be set as the suspension 6 excellent in cost performance.
Further, since a plurality of holes (not shown) are formed in the guide 28, air is not compressed in the cylinder 15 by air flowing through the holes even when the rod 23 reciprocates. The damping force can be stabilized by reducing the air spring effect.
The cases 19 and 20 are each formed with a fitting surface 22, and the friction member 21 is formed with a contact surface 27 that fits the fitting surface 22. For this reason, since the friction member 21 is dragged by the vertical movement of the rod 23 and the contact surface 27 contacts and engages with the fitting surface 22, the friction member 21 can be squeezed in the radial direction. The rod 23 can obtain a stronger frictional force, that is, a damping force.
In the suspension 6, the length of the friction member 21 is appropriately changed and adjusted within a range that does not depart from the gist according to the amplitude of the water tank 5, the length of the rod 23, or the timing of the amplitude to be suppressed. Is possible.

<Second embodiment>
Next, a second embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the location similar to the said 1st Example, and the detailed description is abbreviate | omitted.
In the suspension 40 of the present embodiment, the rod 41 is formed so as to have a large-diameter portion 41a whose outer diameter gradually increases in the axial direction at the tip portion (the upper end portion in FIG. 4).
According to such a configuration, the same effect as in the first embodiment can be obtained, and when the cylinder 15 and the rod 41 vibrate in a direction away from each other, the large-diameter portion 41a portion of the rod 41 is a friction member. Since it comes in contact with the inner peripheral surface of 21, the clearance between them is further reduced, and a greater damping force can be obtained. In a general drum-type washing machine, since the water tank 5 often moves upward and hits the outer box 1, the above structure suppresses the upward movement of the water tank 5. It is possible to prevent the water tank 5 from hitting the outer box 1.

<Third embodiment>
Next, a third embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the location similar to the said 2nd Example, and the detailed description is abbreviate | omitted.
In the suspension 50 of the present embodiment, the spring 51 is disposed between the guide 28 (the upper surface thereof) and the end of the cylinder 15 inside the cylinder 15.
According to such a configuration, the same effects as those of the first and second embodiments can be obtained, and both the cylinder side spring receiving portion 16 and the rod side spring receiving portion 29 are not required. The number of parts constituting 50 can be reduced. In addition, since no members are disposed outside the cylinder 15, the suspension 50 can be reduced in size.
In the rod 41 in the second and third embodiments, the change in the diameter of the large diameter portion 41a can be changed as appropriate.
<Fourth embodiment>
Next, a fourth embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the location similar to the said 1st Example, and the detailed description is abbreviate | omitted.
In the suspension 60 of the present embodiment, the rod 61 is composed of a rod 61A located above and a rod 61B located below across a guide 62 disposed in place of the bearing 17. These rods 61A and 61B are integrated by welding, for example. The guide 62 disposed on the lower side is the same as the guide 28 disposed on the upper side, and is fixed in advance to the rod 61B before welding.
According to such a configuration, the same effect as in the first embodiment can be obtained, and the guide 28 and the guide 62 are used as members that support the rod 61 on both sides with the friction member 21 interposed therebetween. Therefore, compared to the case where the bearing 17 is used on one side, the suspension 60 can be further improved in cost.
Note that the rod 61A and the rod 61B may be integrated with each other by forming a screw and a screw hole. Further, the guide 62 may be fixed in advance to the rod 61A.

<Fifth embodiment>
Next, a fifth embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the location similar to the said 4th Example, and the detailed description is abbreviate | omitted.
In the suspension 70 of the present embodiment, the rod 71 includes an upper rod 71A and a lower rod 71B, and the upper rod 71A has large diameter portions 71a and 71b whose outer diameters gradually increase at both ends in the axial direction. It is formed to have.
According to such a configuration, the same effect as in the first and fourth embodiments can be obtained, and when the amplitude of the water tank 5 increases vertically, the friction member 21 and the rod 71 (rod) both vertically. 71A) can be reduced, and a large damping force can be exerted to further suppress the amplitude.

<Sixth embodiment>
Next, a sixth embodiment of the present invention will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the location similar to the said 5th Example, and the detailed description is abbreviate | omitted.
The suspension 80 of this embodiment has two springs 81 and 82, and these two springs 81 and 82 are located between the guide 28 (the upper surface thereof) and the upper end of the cylinder 15 inside the cylinder 15. And between the guide 72 (the lower surface thereof) and the lower end of the cylinder 15, respectively.
According to such a configuration, the same effect as in the first and third embodiments can be obtained, and the water tank 5 moves upward by making the spring constants of the two springs 81 and 82 different from each other. It can be adjusted so that a different damping force can be obtained depending on whether or not it moves downward.

1 shows a first embodiment of the present invention, and is a broken side view of a suspension. Longitudinal side view of drum washer / dryer Diagram showing the relationship between rod displacement and damping force FIG. 1 equivalent view showing the second embodiment FIG. 1 equivalent view showing the third embodiment FIG. 1 equivalent view showing the fourth embodiment FIG. 1 equivalent view showing the fifth embodiment FIG. 1 equivalent view showing the sixth embodiment Longitudinal side view showing a conventional example The figure which shows the relationship between damping force and drum rotation frequency in the conventional suspension

Explanation of symbols

  In the drawings, 5 is a water tank, 6 is a suspension, 7 is a drum, 15 is a cylinder (cylindrical member), 17 is a bearing, 17a is a shaft insertion hole, 21 is a friction member, 23 is a rod, 28 is a guide, 30 is a spring. , 40 is a suspension, 41 is a rod, 41a is a large diameter part, 50 is a suspension, 51 is a spring, 60 is a suspension, 61 is a rod, 62 is a guide, 70 is a suspension, 71 is a rod, 71a and 71b are large diameter parts , 72 are guides, 80 is a suspension, and 81 and 82 are springs.

Claims (5)

In a drum-type washing machine having a suspension for vibration-proofing a water tank containing a drum,
The suspension is
A tubular member;
A bearing which is supported and fixed inside the cylindrical member and has a shaft insertion hole in the center,
A rod inserted into the shaft insertion hole and supported so as to be capable of reciprocating relative to the bearing;
A cylindrical friction member that is fitted to the outer periphery of the rod inside the cylindrical member and attenuates the amplitude of the water tank by a frictional force with the rod generated by the relative movement of the rod;
A spring disposed between the cylindrical member and the rod;
The cylindrical member is attached to the rod so as to move integrally with the rod, with the friction member being sandwiched between the outer peripheral surface and the inner peripheral surface of the cylindrical member. A drum-type washing machine comprising a guide that contacts the drum-type washing machine.   The drum type washing machine according to claim 1, wherein the rod is formed so that an outer diameter thereof gradually changes in an axial direction.   3. The drum type washing machine according to claim 2, wherein the spring is disposed between the guide and an end of the cylindrical member inside the cylindrical member.   The drum type washing machine according to claim 1, wherein the bearing is composed of a guide similar to the guide. The drum type washing machine according to claim 4, wherein the springs are respectively disposed between the guide and upper and lower end portions of the cylindrical member inside the cylindrical member.

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