JP2010194025A - Washing machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve vibration performance on various floor for installing having different rigidity. <P>SOLUTION: A washing machine includes a damping means 41 for reducing vibration of an outer frame 30 of the washing machine, wherein the damping means 41 includes a cylinder 42 forming a sealed space and a weight 43 reciprocating inside the cylinder 42. The weight 43 includes a passage 44 allowing air to flow in and out. Thereby, vibration is reduced by the damping means 41 when an outer tub 33 vibrates violently by an eccentric load of laundry and the vibration is transmitted to the outer frame 30 of the washing machine, which may cause the outer frame 30 of the washing machine to vibrate. The damping means 41 can reduce an increased range of frequencies, so that vibration of the outer frame 30 of the washing machine is reduced even when resonance frequency of the outer frame 30 of the washing machine changes dependent on an installed place. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention is a laundry for washing, rinsing and dewatering (may be further performed until drying) in a washing and dehydrating tub rotatably disposed in an outer tub elastically supported in the washing machine body. Related to the machine.

  Conventionally, this type of washing machine suppresses a large vibration of the outer tub at the time of dehydration activation due to an eccentric load of clothes and reduces a vibration of the main body (for example, see Patent Document 1).

FIG. 12 shows an overall configuration of a conventional washing machine described in Patent Document 1. As shown in FIG. As shown in FIG. 12, an outer tub 33 elastically supported by the washing machine outer frame 30, a washing / dehydration tub 34 rotatably provided in the outer tub 33, and the washing / dehydration tub 34 are rotated. With the drive means 35 and the vibration damping means 41 provided on the upper part 30a of the washing machine outer frame, the outer tub vibrates violently due to the eccentric load of the laundry, and the vibration is transmitted to the washing machine outer frame 30. Thus, even if the washing machine outer frame 30 tries to vibrate, the vibration is reduced by the vibration damping means 41, and the washing machine outer frame 30 can maintain a state close to being stationary.
JP-A-5-131075 JP 2006-204564 A

  However, in the conventional configuration, the vibration frequency to be damped is limited to some extent as shown in FIG. 2 due to the spring constant of the elastic body 45 of the vibration damping means of FIG. Vibration increases. Since the resonance frequency of the outer frame of the washing machine changes depending on the rigidity of the installation floor, there is a problem that vibration is not reduced depending on the installation location.

  The present invention solves the above-described conventional problems, and provides a washing machine that expands the frequency for reducing the vibration of the outer frame of the washing machine and improves the vibration performance on various installation floors having different rigidity. Objective.

  In order to solve the above-described conventional problems, the washing machine of the present invention includes vibration damping means for reducing vibration of the outer frame of the washing machine, and the vibration damping means supports both ends of the weight with damping and elastic bodies. .

  As a result, the outer tub vibrates violently due to the eccentric load of the laundry, and even if the vibration is transmitted to the washing machine outer frame and the washing machine outer frame tries to vibrate, the vibration is reduced by the damping means, and various installations with different rigidity The vibration performance on the floor can be improved.

  The washing machine of the present invention is a small control means, and the vibration of the washing machine outer frame due to the eccentricity of the laundry can be greatly reduced even on various installation floors having different rigidity such as a wooden floor. Moreover, since the damping means can produce damping and rigidity with the weight and the cylinder, the vibration performance can be improved at low cost and in a compact manner.

A first invention includes an outer tub elastically supported by a washing machine outer frame, a washing / dehydrating tub rotatably provided in the outer tub, a driving means for rotating the washing / dehydrating tub, and a washing machine outer frame And a damping means for reducing vibration of the outer frame of the washing machine, the damping means comprising a cylinder that forms a sealed space and a weight that reciprocates within the cylinder, and air flows into the weight. By providing a flow path that can be inserted, the outer tub vibrates violently due to the eccentric load of the laundry, and even if the vibration is transmitted to the washing machine outer frame and the washing machine outer frame tries to vibrate, the vibration is reduced by the damping means. The Further, since the frequency range that can be controlled by the damping of the vibration control means is expanded, the vibration of the washing machine outer frame can be reduced even if the resonance frequency of the washing machine outer frame changes depending on the installation location.

  In the second invention, in particular, the control means according to the first invention is based on the weight of the weight and the flow of air in and out of the cylinder caused by the reciprocating motion of the weight by supporting both ends of the weight and the cylinder with an elastic body. The operating frequency determined by the dynamic air spring constant and the stiffness coefficient of the elastic body can be adjusted by the stiffness of the elastic body. Thus, the damping coefficient can be determined by the diameter of the air hole provided in the weight, and the operating frequency of the damping means can be set to the resonance frequency of the washing machine outer frame with the elastic body. It can be maximized.

  According to a third aspect of the invention, in particular, the vibration damping means of the second aspect of the invention provides an elastic body at both ends in the cylinder so that the weight of the weight can be reduced when the elastic body collides with the weight. The operating frequency determined by the dynamic air spring constant due to the flow of air in and out of the cylinder caused by the reciprocating motion of the weight and the stiffness coefficient of the elastic body can be switched. One is set to the resonance frequency of the outer tub at the start of dehydration, and the other is set to the resonance frequency of the washing machine outer frame. As a result, the vibration of the outer frame of the washing machine due to the resonance of the outer tub at the start of dehydration and the resonance of the outer frame of the washing machine due to the installation location near the dehydration steady state can be reduced at the same time. The vibration of the outer frame can be reduced.

  According to a fourth aspect of the invention, in particular, the vibration damping means of the second aspect of the invention provides an elastic body at both ends of the weight, so that the weight of the weight when the elastic body and the cylinder inner surface collide with each other, The operating frequency determined by the dynamic air spring constant due to the flow of air in and out of the cylinder caused by the reciprocating motion of the weight and the stiffness coefficient of the elastic body can be switched. One is set to the resonance frequency of the outer tub at the start of dehydration, and the other is set to the resonance frequency of the washing machine outer frame. As a result, the vibration of the outer frame of the washing machine due to the resonance of the outer tub at the start of dehydration and the resonance of the outer frame of the washing machine due to the installation location near the dehydration steady state can be reduced at the same time. The vibration of the outer frame can be reduced.

  According to the fifth aspect of the invention, in particular, the vibration damping means of the first aspect of the invention comprises a plurality of weights and a plurality of cylinders. The effect of the vibration means can be further increased, and the vibration control means can be reduced in size.

  In the sixth invention, in particular, the vibration damping means of the fifth invention is composed of weights having different weights, and the dynamic air spring constant due to the weight of the weight and the flow of air in and out of the cylinder caused by the reciprocating motion of the weight. And one of the operating frequencies determined by the stiffness coefficient of the elastic body is set to the resonance frequency of the outer tub at the start of dehydration, and the other is set to the resonance frequency of the outer frame of the washing machine. As a result, the vibration of the outer frame of the washing machine due to the resonance of the outer tub at the start of dehydration and the resonance of the outer frame of the washing machine due to the installation location near the dehydration steady state can be simultaneously reduced. The outer frame vibration at the time can be reduced.

  In the seventh invention, in particular, the vibration damping means of the fifth invention is composed of elastic bodies having different elastic coefficients, and the dynamic air generated by the weight of the weight and the flow of air in and out of the cylinder caused by the reciprocating motion of the weight. One of the operating frequencies determined by the spring constant and the stiffness coefficient of the elastic body is set to the resonance frequency of the outer tub at the start of dehydration, and the other is set to the resonance frequency of the washing machine outer frame. As a result, the vibration of the outer frame of the washing machine due to the resonance of the outer tub at the start of dehydration and the resonance of the outer frame of the washing machine due to the installation location near the dehydration steady state can be reduced at the same time. Can be reduced.

  According to an eighth aspect of the invention, in particular, the vibration damping means according to the sixth aspect of the invention is characterized in that the resonance frequency in the front-rear direction and the left-right direction of the outer frame of the washing machine, Set to the operating frequency determined by the dynamic air spring constant and the stiffness coefficient of the elastic body. Thereby, the vibration of the washing machine outer frame can be reduced in both the front-rear direction and the left-right direction. Moreover, even when the resonance frequency of the washing machine outer frame is different between the front and rear and the left and right directions, the vibration of the washing machine outer frame can be reduced.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a sectional view of a washing machine according to the first embodiment of the present invention.

  In FIG. 1, the washing machine outer frame 30 elastically supports an outer tub 33 by four tension springs 31 and two dampers 32. The washing / dehydrating tub 34 is rotatably disposed in the outer tub 33. The motor (driving means) 35 is composed of a brushless DC motor and is controlled by an inverter so that the rotational speed can be freely changed. Then, the washing / dehydrating tub 34 is directly driven. The water supply means 36 supplies water into the washing / dehydrating tub 34. The water level detection means 37 detects the washing water level in the outer basket 33. The drainage means 38 drains the washing water in the outer tub 33. The control device 39 is provided at the lower front portion of the washing machine outer frame 30. The control device 39 sequentially controls each step of washing, rinsing and dehydration based on the setting contents inputted by the operation display means 40 provided on the upper front surface of the washing machine outer frame 30. The power switching means (FIG. The motor 35, the water supply means 36, the drainage means 38, etc. are sequentially controlled via a not-shown). The damping means 41 is fixed to the back side of the upper part 30a of the washing machine outer frame. The vibration control means 41 includes a cylinder 42 that forms a sealed space, and a weight 43 that is provided with a flow path capable of flowing in and out of air that reciprocates within the cylinder 42. As the weight 43, an iron weight having a weight of 1 kg is used. As the weight 43 reciprocates within the cylinder 42, air flows into and out of the cylinder. The dynamic air spring constant at that time is 6.6 [N / mm], and the viscous damping coefficient is 0.01 [N · s / mm]. The cylinder 42 is provided with a pair of fixing holes 42c for attaching the damping means 41 to the upper part 30a of the washing machine outer frame. The damping means 41 uses the fixing holes 42c to provide the upper part 30a of the washing machine outer frame. It is screwed to.

  About the washing machine comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  First, after putting clothes and detergent into the washing and dewatering tub 34, the operation display means 40 is operated to start operation. As a result, the water supply means 36 operates, the washing water is supplied into the washing / dehydrating tub 34, and the washing / dehydrating tub 34 also starts rotating. When the specified amount of washing water is supplied, the water supply means 36 stops water supply. By the rotation of the washing and dewatering tub 34, the detergent is dissolved in the washing water and becomes a washing liquid and penetrates into the clothes. The washing and dewatering tub 34 rotates at a low speed of about 30 r / min, and performs washing for a specified time to lift and drop the clothes. After the washing is finished, the drainage means 38 is operated, and the washing liquid in which the dirt is dissolved is drained out of the outer tub 33. After the drainage is completed, the rotation of the washing and dewatering tank 34 is gradually increased. When the vibration frequency due to the rotation of the washing and dewatering tub 34 approaches the resonance frequency (240 to 300 rpm) of the outer tub 33, the outer tub 33 vibrates greatly. This vibration energy is transmitted through the elastic support portions such as the tension spring 31 and the damper 32, and the washing machine outer frame 30 is vibrated greatly as shown in FIG. Further, when the rotation of the washing and dewatering tub 34 rises and approaches the resonance frequency (600 to 900 rpm) of the washing machine outer frame 30, the washing machine outer frame 30 vibrates greatly. The vibration energy of the washing machine outer frame 30 is consumed to vibrate the weight 43, and as a result, the vibration of the washing machine outer frame 30 is reduced. As shown in FIG. 2, the vibration of the washing machine outer frame 30 is reduced over a wide range of 700 to 1000 rpm.

  As described above, in the present embodiment, the washing machine is installed in various different rigidity such as a wooden floor to a concrete floor, and the vibration of the washing machine outer frame 30 is reduced even if the resonance frequency of the washing machine outer frame 30 changes. can do.

(Embodiment 2)
FIG. 3 shows a cross-sectional view of a washing machine according to the second embodiment of the present invention.

  In FIG. 3, the vibration damping means 41 includes a cylinder 42 forming a cylinder space 42a, a weight 43, and an elastic body 45. In the cylinder space 42a, both ends of the weight 43 and the cylinder 42 are supported by an elastic body 45. By adjusting the rigidity of the elastic body 45, the weight of the weight 43 and the operating frequency determined by the dynamic air spring constant caused by the inflow and outflow of air in the cylinder 42a caused by the reciprocating motion of the weight 43 and the rigidity constant of the elastic body 45 are adjusted. The resonance frequency (600 to 900 rpm) of the washing machine outer frame 30 is set. Thus, the damping coefficient is determined by the diameter of the air hole 44 provided in the weight 43, and the operating frequency of the vibration damping means 41 can be set to the resonance frequency of the washing machine outer frame 30 by the rigidity of the elastic body 45. The damping effect of the damping means can be maximized.

(Embodiment 3)
FIG. 4 shows a sectional view of the vibration damping means in the third embodiment of the present invention.

  In FIG. 4, the vibration damping means 41 includes a cylinder 42 that forms a cylinder space 42 a, a weight 43, an elastic body 45, and an elastic body 46. By providing the elastic body 46 at both ends in the cylinder 42, the spring constant in the cylinder is switched between when the elastic body 46 and the weight 43 collide with each other. When the weight 43 does not collide with the elastic body 46, the resonance frequency is the weight of the weight 43 and the dynamic air spring constant due to the flow of air in and out of the cylinder 42 caused by the reciprocating motion of the weight 43. Further, when the weight 43 collides with the elastic body 46, the resonance frequency is determined by the weight of the weight 43 and the stiffness coefficient of the elastic body 46. Therefore, the operating frequency can be switched between when the elastic body 46 and the weight 43 collide with each other and when they do not collide. One operating frequency is set to a frequency (240 to 300 rpm) at which the washing machine outer frame 30 vibrates greatly when the outer tub 33 vibrates greatly. The other operating frequency is set to the resonance frequency (600 to 900 rpm) of the washing machine outer frame. Then, as shown in FIG. 5, the vibration of the washing machine outer frame 30 can be reduced at the frequencies (240 to 300 rpm and 600 to 900 rpm) at which the washing machine outer frame 30 vibrates greatly.

  Thereby, even if it installs variously in which rigidity differs, such as a wooden floor to a concrete floor, the vibration of the washing machine outer frame 30 can be reduced from dehydration start to steady state.

(Embodiment 4)
FIG. 6 shows a sectional view of the vibration damping means in the fourth embodiment of the present invention.

In FIG. 6, the vibration damping means 41 includes a cylinder 42 that forms a cylinder space 42 a, a weight 43, an elastic body 45, and an elastic body 46. By providing the elastic body 46 at both ends of the weight 43, the spring constant in the cylinder is switched between when the elastic body 46 and the inner surface of the cylinder 42 collide with each other. When the elastic body 46 does not collide with the inner surface of the cylinder 42, the resonance frequency is the weight of the weight 43 and the dynamic air spring constant due to the flow of air in and out of the cylinder 42 caused by the reciprocating motion of the weight 43. Further, when the elastic body 46 collides with the inner surface of the cylinder 42, the resonance frequency is determined by the weight of the weight 43 and the rigidity coefficient of the elastic body 46. Therefore, the operating frequency can be switched between when the elastic body 46 collides with the inner surface of the cylinder 42 and when it does not collide. One operating frequency is set to a frequency (240 to 300 rpm) at which the washing machine outer frame 30 vibrates greatly when the outer tub 33 vibrates greatly. The other operating frequency is set to the resonance frequency (600 to 900 rpm) of the washing machine outer frame. Then, as shown in FIG. 5, the vibration of the washing machine outer frame 30 can be reduced at the frequencies (240 to 300 rpm and 600 to 900 rpm) at which the washing machine outer frame 30 vibrates greatly.

  Thereby, even if it installs variously in which rigidity differs, such as a wooden floor to a concrete floor, the vibration of the washing machine outer frame 30 can be reduced from dehydration start to steady state.

(Embodiment 5)
FIG. 7 shows a cross-sectional view of the vibration damping means in the fifth embodiment of the present invention.

  In FIG. 7, the vibration damping means 41 includes a cylinder 42 forming a cylinder space 42a and 42b, and a weight 43a and a weight 43b. The weight 43a and the weight 43b have the same weight of 500 g, and the weight 43a reciprocates in the cylinder 42a. At this time, the dynamic air spring constant due to the inflow / outflow of air is 3.3 [N / mm], and the viscous damping coefficient is 0.01 [N · s / mm]. Also in this configuration, the vibration of the washing machine outer frame 30 is reduced over a wide range of 700 to 1200 rpm as shown in FIG.

  Accordingly, even if a plurality of cylinders are combined and a small and light weight is combined, the washing machine can be installed in various different rigidity such as a wooden floor to a concrete floor, and the washing machine can be changed even if the resonance frequency of the washing machine outer frame 30 changes. The vibration of the outer frame 30 can be reduced, and the vibration damping means 41 can be attached to a place where the installation space in the washing machine outer frame 30 is small.

(Embodiment 6)
FIG. 9 shows a sectional view of the vibration damping means in the sixth embodiment of the present invention.

  In FIG. 9, the vibration damping means 41 includes a cylinder 42 forming a cylinder space 42a and 42b, and weights 43a and 43b having different weights. The washing machine outer frame 30 vibrates greatly when the outer tub 33 vibrates greatly at the operating frequency determined by the weight of the weight 43a and the dynamic air spring constant caused by the flow of air in and out of the cylinder 42a caused by the reciprocating motion of the weight 43a. Set to a frequency (240 to 300 rpm). The operating frequency determined by the weight of the other weight 43b and the dynamic air spring constant due to the inflow and outflow of air in the cylinder 42b caused by the reciprocating motion of the weight 43b is set to the resonance frequency (600 to 900 rpm) of the washing machine outer frame 30. Set. As a result, as shown in FIG. 5, the vibration of the washing machine outer frame 30 can be reduced at the frequencies (240 to 300 rpm and 600 to 900 rpm) at which the washing machine outer frame 30 vibrates greatly.

  Thereby, even if it installs variously in which rigidity differs, such as a wooden floor to a concrete floor, the vibration of the washing machine outer frame 30 can be reduced from dehydration start to steady state.

(Embodiment 7)
FIG. 10 shows a sectional view of the vibration damping means in the seventh embodiment of the present invention.

In FIG. 10, the vibration damping means 41 includes a cylinder 42 forming a cylinder space 42a and 42b, a weight 43a and a weight 43b, and an elastic body 45. In the cylinder space 42a, both ends of the weight 43a and the cylinder 42 are supported by an elastic body 45. The operating frequency determined by the weight of the weight 43a and the dynamic air spring constant caused by the inflow and outflow of air in the cylinder 42a caused by the reciprocating motion of the weight 43a and the rigidity constant of the elastic body 45 is set to the resonance frequency (600 of the washing machine outer frame 30). ~ 900 rpm). The operating frequency determined by the weight of the other weight 43b and the dynamic air spring constant due to the flow of air in and out of the cylinder 42b caused by the reciprocating motion of the weight 43b greatly vibrates the outer tub 33, thereby the washing machine outer frame 30. Is set to a frequency (240 to 300 rpm) at which the vibration is greatly vibrated. As a result, as shown in FIG. 5, the vibration of the washing machine outer frame 30 can be reduced at the frequencies (240 to 300 rpm and 600 to 900 rpm) at which the washing machine outer frame 30 vibrates greatly.

  Thereby, even if it installs variously in which rigidity differs, such as a wooden floor to a concrete floor, the vibration of the washing machine outer frame 30 can be reduced from dehydration start to steady state.

(Embodiment 8)
FIG. 11 shows a sectional view of the vibration damping means in the eighth embodiment of the present invention.

  In FIG. 11, the vibration damping means 41 includes a cylinder 42 forming a cylinder space 42a and 42b, a weight 43a and a weight 43b, an elastic body 45a and an elastic body 45b. In one cylinder space 42a, both ends of the weight 43a and the cylinder 42 are supported in the front-rear direction of the elastic body 45a. In the other cylinder space 42b, both ends of the weight 43b and the cylinder 42 are moved in the left-right direction with the elastic body 45b. It is supported by.

  The operating frequency determined by the weight of the weight 43a and the dynamic air spring constant due to the inflow and outflow of air in the cylinder 42a caused by the reciprocating motion of the weight 43a and the stiffness coefficient of the elastic body 45a is the resonance in the longitudinal direction of the washing machine outer frame 30. Set to frequency (600-900 rpm). The operating frequency determined by the weight of the other weight 43b, the dynamic air spring constant due to the flow of air in and out of the cylinder 42b caused by the reciprocating motion of the weight 43b, and the stiffness coefficient of the elastic body 45b is determined by the left and right sides of the washing machine outer frame 30. The resonance frequency in the direction (600 to 900 rpm) is set.

  Thereby, even if it installs variously in rigidity, such as a wooden floor to a concrete floor, the vibration of the washing machine outer frame 30 can be reduced both in the front-rear direction and the left-right direction.

  As described above, the washing machine according to the present invention can reduce the vibration of the washing machine outer frame 30 even if the washing machine is installed in various ways having different rigidity, such as a wooden floor and a concrete floor.

Sectional drawing of the washing machine in Embodiment 1 of this invention Vibration amplitude characteristic diagram of washing machine outer frame of washing machine in embodiment 1 of the present invention Sectional drawing of the washing machine in Embodiment 2 of this invention Sectional drawing of the damping means in Embodiment 3 of this invention Vibration amplitude characteristic diagram of washing machine outer frame of washing machine in embodiment 3 of the present invention Sectional drawing of the damping means in Embodiment 4 of this invention Sectional drawing of the vibration suppression means in Embodiment 5 of this invention Vibration amplitude characteristic diagram of washing machine outer frame of washing machine in embodiment 5 of the present invention Sectional drawing of the damping means in Embodiment 6 of this invention Sectional drawing of the vibration suppression means in Embodiment 7 of this invention Sectional drawing of the damping means in Embodiment 8 of this invention Cross section of a conventional washing machine

DESCRIPTION OF SYMBOLS 30 Washing machine outer frame 30a Upper part of washing machine outer frame 33 Outer tub 34 Washing and dewatering tub 35 Driving means 41 Damping means 42 Cylinder 43 Weight 45 Elastic body

Claims (8)

An outer tub elastically supported by the outer frame of the washing machine, a washing / dehydrating tub rotatably provided in the outer tub, a driving means for rotating the washing / dehydrating tub, and an upper part of the outer frame of the washing machine And a damping means for reducing vibration of the outer frame of the washing machine, wherein the damping means comprises a cylinder that forms a sealed space and a weight that reciprocates within the cylinder, and air flows into the weight. A washing machine with a flow path that can be entered. The washing machine according to claim 1, wherein the vibration damping means supports both ends of the weight and the cylinder with an elastic body. The washing machine according to claim 1 or 2, wherein elastic bodies are provided at both ends in the cylinder. The washing machine according to claim 1 or 2, wherein elastic bodies are provided at both ends of the weight. The washing machine according to any one of claims 1 to 4, wherein the control means includes a plurality of cylinders and weights. 6. The washing device according to claim 5, wherein the vibration damping means includes a plurality of cylinders and weights having different weights, and each has a resonance frequency determined by a weight coefficient of the weight and a rigidity coefficient in the cylinder due to the reciprocating motion of the weights. Machine. The vibration damping means is composed of a plurality of cylinders and weights, and in each cylinder, the stiffness coefficient due to the reciprocating motion of the weight is set to a different value, and the weight coefficient of the weight and the stiffness coefficient within the cylinder due to the reciprocating motion of the weight are set. 6. The washing machine according to claim 5, wherein the resonance frequencies determined by are different from each other. The washing machine according to any one of claims 1 to 7, wherein the vibration damping means is installed in the front-rear direction and the left-right direction.