JP2013070832A - Drum type washing and drying machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drum-type washer or a drum-type washing and drying machine with low vibration of the vibration part as well as high rigidity of an outer tank without enlarging the outer tank.SOLUTION: A drum-type washer comprises a vibration part 200 comprising a drum 21, an outer tank 23, weights 28a and 28b, and a motor 22. The vibration part 200 is supported by vibration reduction and supporting means in a casing. The outer tank 23 can be splittable into a tub cover 23b and a water tank 23c at a split plane A-A. The water tank 23c comprises a suspension 26 at its bottom serving as the vibration reduction and supporting means. At least a part of the weight 28b, which is positioned at a level lower than the rotation axis Az of the drum, is arranged at between the split plane A-A of the tub cover 23b and the water tank 23c and the suspension 26 at a side of the water tank 23c.

Description

  The present invention relates to a drum-type washing machine and a washing / drying machine.

  In the drum-type washing / drying machine, when the clothes distribution in the drum is uneven, vibration is generated when the drum rotates. This vibration is caused by a vibration part made up of parts having a large mass such as a drum, an outer tub, and a motor. When the drum rotational speed is sufficiently low with respect to the rigidity of the vibration part, the parts constituting the vibration part vibrate together. In order to reduce such vibration, it is necessary to appropriately arrange the mass, the moment of inertia, and the position of the center of gravity of the vibration part. In Patent Document 1 below, in order to easily set the position of the center of gravity of the vibrating part, a drum-type laundry dryer in which a weight for the counterweight is provided in the outer tub so as to be positioned forward of the center part in the front-rear direction of the drum The machine is listed.

Japanese Patent Application Laid-Open No. 2000-262796

  In the conventional drum-type washing and drying machine described above, the center of gravity of the vibrating part made up of large parts such as the drum, outer tub, and motor is provided by providing a weight to the outer tub so as to be ahead of the center in the longitudinal direction of the drum. Easy to set up. In addition, the distance between the weight and the center of gravity of the vibration part is increased, which contributes to increasing the moment of inertia around the center of gravity of the vibration part.

  However, there is a problem that the rigidity of the outer tub is lowered by providing the weight in front of the outer tub in this way. The rigidity of the outer tub and the maximum dewatering rotation speed are closely related, and it is necessary to ensure the rigidity of the outer tub in order to improve the dewatering performance. Methods to increase the rigidity of the outer tub include increasing the plate thickness of the outer tub and adding a reinforcing shape such as a rib to the outer tub. This is not appropriate when considering installation in a general house, which is a limited space. Therefore, there is a need for a method that increases the rigidity of the outer tub and reduces vibrations, regardless of these methods.

  An object of the present invention is to provide a drum-type washing / drying machine having a weight and capable of realizing low vibration and high rigidity at the same time.

  Fixed to the outer tank, a drum that is inclined so that the rotation axis is horizontal or the opening is high, an outer tank that can be divided into a tank cover and a water tank, a housing that holds the lower part of the water tank by vibration-proof support means, and In a drum-type washer / dryer comprising a weight and a motor for rotationally driving the drum, the water tank is provided with at least a part of the weight below the drum rotation shaft, the dividing surface of the outer tank, and the vibration-proof support means. Provide between.

  ADVANTAGE OF THE INVENTION According to this invention, the drum type washing machine and washing-drying machine which simultaneously implement | achieve the low vibration and high rigidity of an outer tub can be provided.

1 is an external perspective view of a drum type washing and drying machine showing an embodiment of the present invention. It is a schematic diagram of the left side surface which shows the internal structure of the drum type washing-drying machine shown in FIG. It is a schematic diagram of the right side which shows the internal structure of the drum type washing-drying machine shown in FIG. FIG. 2 is a right side partial cross-sectional view showing an extracted vibration portion and vibration-proof support means of the drum type washing and drying machine shown in FIG. 1. It is a schematic diagram which shows the fall state of the laundry in the drum under washing. It is sectional drawing which shows typically the division part vicinity of the outer tank shown in FIG. It is a schematic diagram which shows the relationship between the vibration state of an outer tank, and the clearance gap between an outer tank and a housing. It is a schematic diagram which shows the relationship between a metal mold | die and a draft in plastic injection molding. It is a schematic diagram which shows the relationship between a drum rotational speed and the vibration mode of an outer tank and a drum. It is a schematic diagram which shows the relationship between the attachment position of a weight and the inertia moment of a vibration part. It is a schematic diagram which shows the relationship between the attachment position of a weight and the rigidity of an outer tank. It is a schematic diagram which shows the attachment position of a weight, the rigidity of an outer tank, and the relationship of a vibration.

  Embodiments of the present invention will be described below with reference to the drawings.

  FIG. 1 is an external perspective view of a drum type washing and drying machine showing an embodiment of the present invention. FIG. 2 is a schematic diagram of the left side view showing the internal structure of the drum type washing and drying machine shown in FIG. FIG. 3 is a schematic diagram of the right side surface showing the internal structure of the drum type washing and drying machine shown in FIG. 1. In the following description, the front / rear / left / right / up / down directions are based on the directions shown in FIG. 1 that correspond to the front / rear / right / left / up / down directions when the washing / drying machine 100 of the present invention is installed on a horizontal plane.

  As shown in FIG. 1, a washing / drying machine 100 according to the present embodiment includes a housing 1 that forms an outer shell thereof. The housing 1 forms a box shape with a base 1g having left and right side plates 1a and 1b, a front cover 1c, a back cover 1d, an upper cover 1e, a lower front cover 1f, and rubber feet 1h (see FIG. 2). It has sufficient strength. The size of the chassis 1 is represented by a chassis width dimension W1, a chassis depth dimension D1, and a chassis height dimension H1.

  At the approximate center of the front cover 1c, a loading port 1i for taking in and out the laundry is formed. The loading port 1i is mainly formed of a transparent resin and is a door 3 that can be visually recognized in the washing and drying machine 100. Is provided. The door 3 is attached to a front reinforcing member 2a (see FIG. 2), which will be described later, via a hinge (not shown) so that it can be opened and closed. A door opening lever 3a provided on the outer edge of the door 3 locks / unlocks the door 3. It is opened by releasing the locked state (not shown). Further, the door 3 is pressed toward the front cover 1c by the user, and is locked by the above-described lock / unlock mechanism (not shown) with the insertion port closed.

  An operation panel 4 is provided at the upper center of the housing 1. The operation panel 4 includes a power switch 4a, an operation switch 4b, and a display 4c. The power switch 4, the operation switch 4 b, and the display 4 c are electrically connected to a control device 5 (see FIG. 2) disposed at the lower part in the housing 1.

  The drum 21 shown in FIG. 2 is a cylindrical washing / dehydrating / drying tub that is rotatably supported, and has a large number of through holes 21e (FIG. 4) for passing water and ventilation through the cylindrical side wall and bottom wall. And an opening 21a (see FIG. 4) for putting clothes into and out of the front end face. A fluid balancer 21c integral with the drum 21 is provided outside the opening 21a. The rear end surface of the drum 21 is provided with a drum flange 21d that is a coupling portion with a motor 22 described later. A plurality of lifters 21b having a convex shape for lifting clothes are provided on the inner wall of the drum 21, and when the drum 21 rotates during washing and drying, the clothes are brought into a cylindrical side wall by the centrifugal force generated by the lifter 21b and rotation. It lifts along and repeats the movement of falling by gravity. The rotation center axis Az of the drum 21 is inclined so that the horizontal or opening 21a side becomes higher.

  Reference numeral 23 denotes a cylindrical outer tub having a back surface, which can hold water. The outer tub 23 contains the drum 21 coaxially, has an opening 21a for putting clothes in and out on the front surface, and a motor 22 is attached to the center of the rear surface via an outer tub flange 23d. A shaft 22 a of the motor 22 passes through the outer tub 23 and is coupled to the drum 21. The outer tub 23 can be divided by a tank cover 23b including an opening 23a and a water tank 23c to which the motor 22 is attached. The opening 23a and the opening provided in the front reinforcing member 2a are connected by a bellows 25, which is an elastic body such as rubber, and the outer tub 23 is water-sealed by closing the door 3. A drain outlet 23e is provided at the bottom of the outer tub 23 and is connected so as to communicate with the drain hose 35.

  Reference numeral 24 denotes a vibration sensor that detects the acceleration of the outer tub 23, and is installed at the center front end of the lower surface of the water tub 23c. The vibration sensor 24 transmits the vibration state of the outer tub 23 to the control device 5, so that it can be operated in accordance with the vibration state of the outer tub 23. The vibration sensor 24 may be of a type that detects the speed or displacement of the outer tub 23.

  28a and 28b are weights for adjusting the mass balance of the outer tub 23, and are provided one above the drum rotation axis Az and two below. The weight below the drum rotation axis Az is provided in front of the water tank 23c as much as possible and symmetrical to the drum rotation axis Az. Details will be described later.

  The outer tub 23 is supported in an anti-vibration manner by a suspension 26 (consisting of a coil spring and a damper) whose lower side is fixed to the base 1g. The upper side of the outer tub 23 is supported by a front auxiliary spring 27a and a rear auxiliary spring 27b (see FIG. 4) attached to an upper reinforcing material (not shown), and prevents the outer tub 23 from falling in the front-rear direction. .

  Denoted at 34 is a detergent container provided on the upper left side in the housing 1 and fixed to the upper reinforcing member of the housing 1. On the rear side of the detergent container 34, there is provided a water supply unit 31 made up of components related to water supply such as an electromagnetic valve, a pump, and a water level sensor. The top cover 1e is provided with a water supply hose connection port 32a from a water tap and a water absorption hose connection port 33a for remaining hot water in the bath. The detergent container 34 is connected to the outer tub 23, and a washing water is supplied to the outer tub 23 by operating a water supply electromagnetic valve (not shown) in the water supply unit 31 or a bath water supply pump (not shown). Supply.

  The drain hose 35 is provided with a circulation pump 35a, a lint filter (not shown), and a drain valve 35b in the middle. The drain valve 35b is closed and supplied with water to collect water in the outer tub 23, and the drain valve 35b is opened. The water in the outer tub 23 is discharged out of the machine.

  The circulation pump 35a has a discharge port to the circulation hose 35c and the detergent dissolving circulation hose 35d, and the discharge port can be switched by switching the rotation direction of the circulation pump 35a. Thereby, it is possible to disperse the detergent and the washing water on the laundry. When dissolving the detergent, the circulation pump 35a is reversely rotated, passes through the detergent dissolving circulation hose 35c, and circulates back to the bottom of the outer tub 23 (the tub cover 23b). At this time, undissolved detergent and water are vigorously stirred in the circulation pump 35a, so that the detergent can be efficiently dissolved and a high-concentration detergent liquid can be generated. On the other hand, the circulation pump 35a is rotated forward during washing. The washing water collected at the bottom of the outer tub 23 passes through the waste filter 23e, passes through the lint filter, enters the circulation pump 35a, passes through the circulation hose 35c, and the sprinkler port (not shown) provided on the upper portion of the tank cover 23b. Water is sprinkled inside and circulates back to the lower part of the outer tub 23. As a result, since the washing water can be uniformly applied to the laundry, high washing power and rinsing performance can be obtained, and a small amount of washing water is circulated by the circulation pump 35a, so that water can be saved for repeated use. .

  3 is a water-cooled dehumidifying mechanism installed vertically inside the back surface of the housing 1, and connects a lower back portion of the outer tub 23 to a blower unit 41b described later, and the outer tub is indicated by an arrow in FIG. The air in 23 can be circulated and dehumidified. Although not shown, the blower unit 41b fixed to the upper reinforcing member is provided with a drying filter, a blower fan, and a heater inside the flow path. The air that has entered the blower unit 41b from the water-cooled dehumidifying mechanism 41a is pressurized by the blower fan with the lint removed by the drying filter, further receives heat from the heater, and is sent into the drum 21. Here, the water-cooled dehumidifying mechanism 41a and the heater 41b are used for dehumidification, but a method using a heat pump instead of the heater 41b or a method of exhausting moist air as it is to dehumidify may be used.

  Next, characteristic components of the washing / drying machine 100 according to the present embodiment will be described with reference to FIG. FIG. 4 shows the configuration of the washing / drying machine 100 according to the present embodiment, such as the drum 21, motor 22, outer tub 23, weight 28, etc. An anti-vibration support means including a spring 27a, a rear auxiliary spring 27b, and a bellows 25 is extracted and shown. As described above, the outer tub 23 can be divided into a tub cover 23b and a water tub 23c. Of the divided surfaces, a surface on which a seating surface for fixing the outer tub 23 and the tub cover 23b is provided is a divided surface. AA. In addition, a straight line that can be drawn in the vertical direction from the point where the central axis of the suspension 26 that is substantially cylindrical and the outer tub 23 intersect is represented by an anti-vibration support shaft B. The anti-vibration support shaft B corresponds to the vertical component of the force that the outer tub 23 receives from the suspension 26.

  First, the drum 21 which is one of the features will be described. The drum diameter D is provided to be as large as possible with respect to the housing width dimension W1. The reason is that the washing of the drum-type washing / drying machine 100 is a “tapping wash” method in which the clothes lifted by the lifter 21 b are dropped by gravity and washed against the cylindrical side wall of the drum 21. This is because the larger the diameter D, the better. On the other hand, the housing width dimension W1 is restricted by its size in consideration of installation property in a general house and user convenience. According to our survey, the ratio of houses that can be installed is 80% when the box width dimension W1 is 670 mm to 700 mm. However, if the box width dimension W1 is 610 mm or less, the ratio that can be installed increases to about 98%. To do. Therefore, for example, if the housing width dimension W1 is 610 mm or less, the drum diameter D is about 500 to 530 mm at the maximum.

  As described above, when the housing width dimension W1 is restricted due to the ease of installation in a general house and the drum diameter D cannot be increased, a high cleaning power can be ensured by extending the drum depth dimension Ld. Two reasons are given below.

  FIG. 5 is a schematic view of the washing in which clothes lifted by the lifter are dropped to perform washing, and shows the relationship between the clothes drop height h and the drum depth dimension Ld. When the drum depth dimension Ld is short as shown in FIG. 5A, the layer that overlaps the cylindrical side wall of the drum 21 becomes thicker, and the drop height h becomes lower. On the other hand, when the drum depth dimension Ld is long as shown in FIG. 5 (b), the clothes are dispersed in the depth direction of the drum and the layers due to the overlap of the clothes are thinned, so the fall height h is high. For this reason, when the depth dimension Ld is increased, the drop height is increased even with the same drum diameter D, so that the cleaning power is improved.

  Further, by increasing the drum volume by extending the drum depth dimension Ld, the clothes in the drum 21 can move more easily, and as a result, dirt can be easily removed. According to our research, if the drum volume is about 72 L or more with a washing substance amount of 9 kg, sufficient detergency can be obtained. For example, if the drum diameter D is 500 to 530 mm, the drum depth Ld is about 360 to 410 mm. This is a drum with a long depth in which the ratio of the drum depth dimension Ld to the drum diameter D exceeds 0.6. The drum volume used here is an actual volume obtained by subtracting the volume of the lifter 21b, the fluid balancer 21c, and the like from the calculated volume obtained from the drum diameter D and the drum depth dimension Ld.

  However, the washing / drying machine 100 having the drum with the long drum depth Ld such that the ratio Ld / D of the drum depth Ld to the drum diameter D exceeds 0.6 can improve the cleaning power. The following effects are given to vibration. By extending the drum depth dimension Ld, the action point of the excitation force when the clothes are biased is likely to act at a position far from the center of gravity, and vibration that causes the front end of the vibration unit 200 to sway is increased. In addition, the left-right displacement of the front end of the vibration part 200 increases as the depth dimension Ld increases. Therefore, the washing / drying machine 100 of the present embodiment having the drum 21 having the long depth dimension Ld is more likely to generate a whirling vibration, that is, a vibration in the rotational direction than the vibration in the translational direction of the vibration unit 200, and the displacement amount is also large. It can be said. In order to reduce such vibration in the rotational direction, it is necessary to increase the moment of inertia of the vibration unit 200.

  Next, the outer tank 23 which is the second feature will be described. A motor 22 is attached to the rear end face of the outer tub 23 via an outer tub flange 23d having sufficient strength. The motor 22 includes a stator 22c fixed to the outer tank flange 23d and a shaft 22a integrated with a rotor 22b provided with a permanent magnet. The shaft 22 a is rotatably supported by a bearing 22 d provided on the outer tub flange 23 d, passes through the center of the back surface of the outer tub 23, and is coupled to the drum flange 21 d of a strength member located on the back surface of the drum 21. .

  Since the outer tub 23 contains the drum 21 as described above, the outer tub 23 can be divided into a tank cover 23b having an opening 23a and a water tank 23c having a motor 22. The water tank 23c has an outer tank flange 23d on the back surface, and is stronger than the tank cover 23b having the opening 23a. Therefore, the suspension 26 on which a large force acts can be provided in the lower part of the water tank 23c. That is, it is possible to prevent the outer tub 23 from being deformed by the reaction force of the suspension 26 by providing at least a part of the vibration isolating support shaft B so as to pass through the water tub 23c having the outer tub flange 23d. Note that, unlike the suspension 26, the spring and the damper do not necessarily have to be integrated, and any anti-vibration support means that can apply a damping force to the outer tub 23 may be used. For example, the structure which supports the lower part of the water tank 23c with the anti-vibration support means which does not include a spring like a damper may be sufficient.

  FIG. 6 is a side sectional view enlarged so as to include a part of the dividing surface AA of the tank cover 23b and the water tank 23c. Ld23b is the distance to the inner wall of the front end face where the opening 23a of the tank cover 23b is located, and Ld23c is the distance to the inner wall of the rear end face of the water tank 23c. The distance from the inner side to the inner side of the rear end surface is Ld23. That is, the sum of Ld23b and Ld23c is Ld23.

  Here, the relationship between Ld23b and Ld23c will be described. FIG. 7 is a top view that focuses on the drum 21, the outer tub 23, and the casing 1 and omits unnecessary portions for explanation in order to explain that the position where the outer tub 23 and the casing 1 are likely to collide varies depending on the position of clothing. FIG. FIG. 7A shows a situation when clothing is biased on the front side of the drum 21, and FIG. 7B shows a situation when clothing is biased on the rear side of the drum 21. Although details of the vibration will be described later, the vibration that the front side of the outer tub 23 swings as shown in FIG. 7A increases due to the rotational speed of the drum 21 and the biased state of the clothing, or the outer tub as shown in FIG. 7B. The vibration which shakes the back side of 23 becomes large. If the vibration is large at this time, the outer tub 23 and the casing 1 may collide and generate noise, so the outer diameters of the front end face and the rear end face of the outer tub 23 need to be set as small as possible. On the contrary, it is the center part in the front-rear direction of the outer tub 23 that can keep the distance from the housing 1 most with respect to the front or rear runout of the outer tub 23, and the front end face or the rear end face of the outer tub 23. Compared with, there is a margin in the gap with the housing 1. Therefore, by setting a split surface AA (see FIG. 6) for screwing the tank cover 23b and the water tank 23c near the center of the outer tank 23 in the front-rear direction, the collision between the outer tank 23 and the casing 1 is prevented. It can be hard to happen. The collision with the casing 1 due to this rotational vibration is likely to occur when the casing width dimension W1 and the drum diameter D are constant and the drum depth dimension Ld is longer. Therefore, in the washing / drying machine 100 having a long depth such that the ratio Ld / D of the drum depth dimension Ld to the drum diameter D exceeds 0.6, the length of Ld23b is 0.8 to 1.2 times that of Ld23c. By doing so, the occurrence of collision between the outer tub 23 and the housing 1 is suppressed as much as possible. For example, in the washer / dryer 100 shown in the present embodiment, Ld23b is set to about 190 mm, and Ld23c is set to about 215 mm.

  In addition to the above, setting the length of Ld23b from 0.8 to 1.2 times that of Ld23c has the following effects. As shown in FIG. 6, the tank cover 23b and the water tank 23c have inner cylindrical walls having gradients θ23b and θ23c with respect to the drum rotation axis Az, and these are provided in the manufacturing process. As shown in FIG. 8, the tank cover 23b and the water tank 23c are injected with a reinforced plastic such as polypropylene containing glass fiber between a male mold 90a forming an inner wall and a female mold 90b forming an external appearance, and are cooled and hardened. Thereafter, the male mold is pulled out in the direction of the arrow in FIG. At this time, by providing a draft angle θ in advance in the male mold 90a and the female mold 90b, it is possible to prevent an excessive force from being applied to the molded product when the male mold 90a is pulled out. However, due to the draft angle θ, the inner diameter of the convex portion 90c of the male mold 90a is reduced, and the gap between the drum 21 and the end surface of the tank cover 23b and the water tank 23c is narrower than that of the dividing surface AA. If the gap between the drum 21 and the outer tub 23 is too small, deformation of the drum 21 or the outer tub 23 and assembly errors cannot be allowed. On the other hand, in terms of space saving, the gap between the drum 21 and the outer tub 23 should be as small as possible. Thus, in order to make the gap between the drum 21 and the outer tub 23 as small as possible, it is necessary to suppress the decrease in the inner diameter due to the draft angle as much as possible. Since the decrease in the inner diameter due to the draft angle is proportional to the depth dimension, by setting the length of Ld23b from 0.8 times to 1.2 times that of Ld23c, both the tank cover 23b and the water tank 23c reduce the inner diameter. Can be small. For example, in the washer / dryer 100 shown in the present embodiment, the depth dimension Ld23c of the water tank 23c is about 215 mm, and the length of the Ld23b is 0.8 to 1.2 times the length of the Ld23c. The depth dimension Ld23b is 172 mm to 258 mm. At this time, if the draft angle θ23b of the tank cover 23b is 1 degree, the decrease ΔD23b in the inner diameter of the tank cover 23b is about 4.5 mm at the maximum. Therefore, the radial gap between the drum 21 and the outer tub 23 must be at least 4.5 mm or more, and the drum diameter D and the outer tub inner diameter may be set so as to allow an error in dimensional accuracy. Further, the front end of the drum 21 is likely to swing around the outer tub 23 by the distance from the bearing 22d (see FIG. 4), and depending on the drum rotation speed, the front end of the drum 21 and the outer tub 23 (the tank cover 23b). The inner wall may collide. Therefore, in order to secure a gap between the front end portion of the drum 21 and the tank cover 23b, it is desirable that Ld23c and Ld23b are substantially the same length or Ld23b is slightly shortened.

  Here, the split surface AA of the tank cover 23b and the water tank 23c will be described. The tank cover 23b and the water tank 23c are provided with grooves and protrusions so as to mesh with each other at the dividing plane AA, and a rubber O-ring (not shown) is sandwiched between them to circulate water in the outer tank. Seal. Furthermore, on the dividing surface AA of the tank cover 23b and the water tank 23c, seat surfaces for screw fastening are provided discretely, and both are fixed by tightening the screw 23g from the tank cover 23c side. To do. For example, considering the strength of plastic, the type of screw 23g is preferably M6 or more. As described above, when the tank cover 23b and the water tank 23c are formed of an isotropic uniform material, they become discontinuous at the joint, so that the mechanical characteristics change at the joint. In other words, the rigidity of the outer tub 23 has an inflection point on the dividing surface of the tub cover 23b and the water tub 23c with respect to the external force.

  Next, the weight 28b which is the third feature will be described. As shown in FIG. 4, in the washing / drying machine 100 according to the present embodiment, at least a part of the weight 28b positioned below the drum rotation axis Az includes a partition surface of the tank cover 23b and the water tank 23c, and a water tank. It is provided between the suspensions 26 on the 23c side. In other words, it suffices that at least a part of the weight 23c is included in the portion surrounded by the broken line in the drawing. The weights 28b may be combined into one in an arc shape, or two or more may be provided. Moreover, it is possible to prevent the weight 28b from colliding with the housing 1 before the outer tank 23 by installing the weight 28b on the inner side in the left-right direction than the outermost diameter of the outer tank 23. In order to explain the effect of placing the weight 23c at this position, the vibration of the washing / drying machine 100 will be described first.

  In the washing / drying machine 100, when the clothes are biased during the dehydrating operation, the vibration behavior changes according to the rotation speed of the drum 21. FIG. 9 is a schematic diagram in which the vibration behavior of the outer tub 23 and the drum 21 is divided into two rotation speed ranges and the scale is adjusted for the sake of simplicity.

  When the rotation speed of the drum 21 increases from the stopped state, for example, at about 100 to 300 rotations per minute, the vibration unit 200 integrally vibrates in the translational direction or the rotational direction of the left, right, up, down, front and back, or the secondary. A resonance mode appears. In the primary and secondary resonance modes, there is no problem even if the components constituting the vibration unit 200 are considered as a rigid body. Therefore, it can be said that the resonance mode is dominated by the mass and moment of inertia of the vibration unit 200. For example, when the moment of inertia of the vibration unit 200 is small with respect to the excitation force, the vibration increases due to the primary and secondary resonance modes, and the outer tub 23 may collide with the inner wall of the housing 1 and generate noise. Particularly, the collision between the outer tub 23 and the inner wall of the casing 1 is caused by vibration that the front side of the vibration part 200 rotates in the left-right direction around the center of gravity of the vibration part 200, in other words, vibration such as swinging. Cheap. In order to reduce such vibration in the rotation direction, it is necessary to increase the moment of inertia of the vibration unit 200. Therefore, means for increasing the moment of inertia of the vibration unit 200 will be described next.

  FIG. 10 is a view of the vibration portion 200 oscillating in the rotation direction, as viewed from the right side. The case where the distance Lw in the front-rear direction from the rotation center O to the weight 28b is long (a), and the case where it is short (b). Represented by In other words, the center of rotation O is a node of whirling vibration, and is different depending on the vibration mode. Of the primary and secondary resonance modes of the vibration part 200, the collision between the outer tub 23 and the inner wall of the housing 1 is likely to occur because the vibration is centered on the vicinity of the center of gravity of the vibration part 200 or the point on the anti-vibration support shaft B. This is when the front side of the unit 200 vibrates so as to shake its head. The center of gravity of the vibration unit 200 is on the rear side of the center of the outer tub 23 in the front-rear direction because heavy objects such as the outer tub flange 23d, the drum flange 21d, and the motor 22 are provided on the rear side. Also, the attachment position of the suspension 26 that holds the vibration unit 200 is located below the center of gravity of the vibration unit 200. Therefore, the rotation center O in FIG. 10 is on the rear side of the center of the outer tub 23 in the front-rear direction. However, when three or more anti-vibration support means such as the suspension 26 are provided, the anti-vibration support shaft B is not necessarily near the center of gravity, but the vibration of the vibration unit 200 where heavy objects concentrate on the rear side is reduced. Therefore, at least one of the vibration isolating support means is necessary on the rear side of the center of the outer tub 23 in the front-rear direction.

  As shown in FIG. 10A, if the distance Lw between the rotation center O and the weight 28b is long, the moment of inertia due to the weight 28b increases, and the vibration in the rotational direction decreases. On the contrary, when Lw is short (b), the moment of inertia becomes small and the vibration in the rotational direction becomes large. That is, it can be said that the vibration of the vibration unit 200 in the primary and secondary resonance modes becomes smaller as the distance Lw in the front-rear direction between the rotation center O and the weight 28b becomes longer.

  When the rotational speed further increases, a tertiary resonance mode in which the drum 21 and the outer tub 23 vibrate separately appears. In this resonance mode, not only the moment of inertia described above but also the rigidity of the vibration part 200 becomes dominant. When the rigidity of the vibration unit 200 is low with respect to the drum rotation speed, separate vibrations such that the outer tub 23 swings around the drum 21 appear as shown in FIG. Noise may be generated due to the collision of the inner wall of the tank 23. In order to prevent such a third resonance mode, the rigidity of the vibration unit 200 may be increased. In particular, it is effective to increase the rigidity of the outer tub 23 in the vibration part 200. This is because the tensile strength of the portion made of a metal material such as the drum 21, the shaft 21a, and the outer tank flange 23d is 200 MPa or more, whereas the tensile strength of the outer tank 23 made of polypropylene containing glass fiber. This is because the strength decreases by about an order of magnitude of about 25 MPa. Next, a method for increasing the rigidity of the outer tub 23 will be described.

  Examples of methods for increasing the rigidity of the outer tub 23 include making the material of the outer tub 23 stronger, increasing the thickness of the outer tub 23, or adding a reinforcing shape such as a rib. However, increasing the rigidity with the material causes an increase in cost, and increasing the rigidity with the outer tank shape increases the size of the outer tank 23. The size of the outer tub 23 is not necessarily appropriate under conditions where it is necessary to accommodate a drum as large as possible in a limited housing size due to the ease of installation in a general house. Therefore, a means for improving the outer tub 23 is required regardless of these. Therefore, a method for increasing the rigidity without changing the dimensions of the outer tub 23 will be described next.

  FIG. 11 shows a force F23b that acts on the mass of the tank cover 23b, a force Fw that the tank cover 23b receives from the weight 28b, and a force F that acts on the screw fastening portion of the dividing surface AA. Note that portions of the vibration unit 200 that are not necessary for the description are omitted. In the tertiary resonance mode, whirling vibration is generated with the support portion of the drum 21 such as the shaft 21a, the drum flange 21d, and the outer tank flange 23d as a fulcrum. As shown in FIG. 11A, when the split surface AA is included between the support portion of the drum 21 and the front and rear direction of the weight 28b, the force F23b acting on the mass of the tank cover 23b and the force Fw received from the weight 28b. The force resulting from the two acts on the vicinity of the screw fastening portion of the dividing surface AA. On the other hand, as shown in FIG. 11B, when the split surface AA is not included between the support portion of the drum 21 and the front and rear direction of the weight 28b, the force related to the vicinity of the screw fastening portion of the split surface AA. Is only the force F23b acting on the mass of the tank cover 23b. When the force applied to the vicinity of the screw fastening portion of the dividing surface AA is large, that is, when stress concentration occurs, the portion is easily broken, and as a result, the rigidity of the outer tub 23 decreases. Therefore, in order to increase the rigidity of the outer tub 23, it is necessary to set the weight 28b closer to the water tub 23c than the dividing surface AA. In other words, when the position of the weight 28b in the front-rear direction is closer to the tank cover 23b than the dividing surface AA, the rigidity of the outer tank 23 is lowered, and conversely, it is higher on the water tank 23c side. Thus, the rigidity of the outer tub 23 tends to have an inflection point on the dividing plane AA with respect to the attachment position of the weight 28b in the front-rear direction.

  FIG. 12 is a diagram schematically illustrating the relationship between the attachment position of the weight 28 b in the front-rear direction, the rigidity of the outer tub 23, and the vibration of the vibration unit 200. The force acting on the screw fastening portion including the split surface AA of the outer tub 23 is schematically represented by (a) to (d) for each attachment position of the weight 28b, and the tendency thereof is summarized in a table (e ). The rotation center of the rotational vibration generated in the primary and secondary resonance modes is the mounting position of the motor 22, and the distance to the weight 28b is represented by Lw. Moreover, the arrow F of FIG. 12 represents what becomes the largest among the forces concerning the junction part of the tank cover 23b and the water tank 23c in division surface AA, The magnitude | size is typically shown by the length of the arrow. It represents.

  First, the rigidity of the outer tub 23 will be described. On the tank cover 23b side with respect to the dividing surface AA, the force applied to the joint between the tank cover 23b and the water tank 23c is increased, including the dividing surface AA between the support portion of the drum 21 and the front and rear direction of the weight 28b. The rigidity improvement effect of the outer tub 23 due to the attachment position of the weight 28b is small. Conversely, on the water tank 23c side from the dividing surface A-A, the force applied to the joint between the tank cover 23b and the water tank 23c is small because the weight 28b is not fixed to the tank cover 23b. The effect of improving the rigidity of the tank 23 is great.

  Next, the vibration of the vibration unit 200 will be described. In order to simplify the explanation, the center of the rotational vibration of the vibration part 200 is assumed to be the attachment part of the motor 22 in FIG. As the attachment position of the weight 28b becomes farther from the center of rotation, the moment of inertia of the vibration unit 200 increases, so that the vibration that causes the front side of the vibration unit 200 to swing its head in the left-right direction is reduced. That is, it can be said that the vibration reduction effect increases as the distance Lw between the rotation center and the weight 28b increases. This tendency is related to the distance Lw between the center of rotation and the weight 28b regardless of the dividing plane AA.

  From the above, the rigidity improvement effect of the outer tub 23 and the vibration reduction effect of the vibration part 200 depending on the attachment position of the weight 28b can be summarized as shown in FIG. In the table of FIG. 12 (e), the rigidity of the outer tub 23 is enhanced and the vibration reduction effect is maximized. The weight 28b is provided on the water tub 23c side in the vicinity of the dividing plane AA. It can be said that this is the configuration. In other words, low vibration and high rigidity can be realized at the same time by providing the weight 28b as far as possible in the water tank 23c. Further, the water tank 23c is provided with a suspension 26 which is a vibration isolating support means, and depending on the vibration mode, vibration occurs in a rotational direction such that the center of rotation is on the vibration isolating support shaft B (see FIG. 4). Since the moment of inertia is determined by the distance between the mass and the center of rotation, even if the weight 28b is mounted on the anti-vibration support shaft B, the effect of increasing the inertia moment in the vibration mode where the anti-vibration support shaft B is the rotation center is I can't hope. Therefore, it is necessary to attach the weight 28b in front of at least the anti-vibration support shaft B.

  Therefore, in the washing / drying machine 100 according to the present embodiment, at least a part of the weight 28b positioned below the drum rotation axis Az is divided into the tank cover 23b and the division surface AA of the water tank 23c, and the water tank 23c side. By providing it between the suspensions 26, both low vibration and high rigidity can be realized. In addition, since the weight 28b is attached to the water tank 23c and is attached further forward, it may be attached so as to straddle the dividing plane AA. By attaching the weight 28b to the water tank 23c in this way, there is no need to attach the weight 28b, which is a heavy object, to the tank cover 23b.

21 drum 22 motor 23 outer tank 23b tank cover 23c water tank 25 bellows 26 suspension 27a front auxiliary spring 27b rear auxiliary spring 28b weight

Claims (3)

Fixed to the outer tank, a drum that is inclined so that the rotation axis is horizontal or the opening is high, an outer tank that can be divided into a tank cover and a water tank, a housing that holds the lower part of the water tank by vibration-proof support means And a motor that rotationally drives the drum,
A drum-type washing machine and a washing machine characterized in that at least a part of the weight below the rotating shaft of the drum is provided between the division surface of the outer tub and the vibration-proof support means in the water tank. Dryer.   The drum-type washing machine and the washing and drying machine according to claim 1, wherein a ratio Ld / D of a depth dimension Ld of the drum and a diameter D of the drum is 0.6 or more.   3. The drum type washing machine and the washing and drying machine according to claim 1, wherein a ratio of a length in the drum rotation axis direction between the tank cover and the water tank is set to 0.8 to 1.2 times.