WO2000029681A1

WO2000029681A1 - Toilet device and toilet device designing method

Info

Publication number: WO2000029681A1
Application number: PCT/JP1999/006401
Authority: WO
Inventors: Noboru Shimbara; Hisato Haraga; Yuichi Furuta; Humitsuki Tanaka; Ryosuke Hayashi; Yasuhiro Yanagawa
Original assignee: Toto Ltd.
Priority date: 1998-11-16
Filing date: 1999-11-16
Publication date: 2000-05-25
Also published as: JP4465881B2; AU1181700A

Abstract

A human body washing device excellent in operability, design feature, feeling of use, and comfortableness even in a restricted toilet room and also easy in design, assembly, and installation, wherein a blower (14) is provided with a fresh air sucking port (14a) and an impeller comprising an impeller support body driven rotatably by a motor (12) and air blowing vanes which are disposed roughly uniformly on the outer periphery of the impeller support body and blow and build up air sucked from the sucking port (14a) by a centrifugal force generated by the rotation of the air blowing vanes, and the air blowing vanes comprise speed increasing vanes (17) which increase the velocity of air flowing in from the air sucking port (14a) to allow it to flow out by reducing the flow path area radially from the center of the impeller support body.

Description

Specification

TECHNICAL FIELD The present invention relates to a toilet apparatus and a method of designing a toilet apparatus.

TECHNICAL FIELD The present invention relates to a toilet device provided with a blower and a method for designing a toilet device. Background art

2. Description of the Related Art Conventionally, as this kind of a human body local cleaning device, a device using an axial fan has been known as disclosed in Japanese Patent Application Laid-Open No. H10-168980. This body part cleaning device attempts to reduce the size of the casing by optimizing the installation conditions. As another conventional technique, as disclosed in Japanese Patent Application Laid-Open No. Hei 6-3131331, by using a common fan for drying and local heating of the buttocks, miniaturization and cost reduction are achieved. Something to measure is also known.

These blowers are used in the toilet room for various applications such as local drying after local washing, deodorization in the toilet room, and air conditioning such as heating and cooling. On the other hand, if these blowers are built into a human body cleaning device in a narrow toilet room, the size of the device itself will increase, resulting in problems such as impaired operability and poor design, and interference with walls and pipes and the device in the first place. In some cases, installation was not possible.

In human body cleaning equipment, vibration is easily transmitted to the human body even from the structural point of view, so if vibration occurs, it gives a more unpleasant feeling than other equipment, so it is necessary to keep the rotation speed of the motor used for the blower low . Generally used centrifugal blowers use the centrifugal force generated by the rotation of the impeller to blow air, so if the rotation speed of the motor is reduced, the impeller and the blower unit become large, and the inside of the human body cleaning device The space occupied by the blowers is very large.

On the other hand, if the blower is forcibly reduced in size in order to reduce the size of the human body local cleaning device, the motor speed will increase unnecessarily, generating large vibrations and noise. This causes a new problem in designing the device. This is more remarkable in high-performance models that have multiple blowers such as drying, deodorizing, and cooling / heating.Because they have multiple blowers, the occupied volume of the blowers becomes very large, and the blowers can be used for multiple purposes. Even if the occupied volume of the blower is reduced by switching the flow path, the blower pipe is long, and the switching mechanism is provided in the middle of the pipe, which increases the pressure loss, resulting in a large blower Since pressure was required, it was necessary to greatly increase the number of revolutions in the evening and to make the blower itself large.

In addition, when the air ducts are routed, the volume occupied by the ducts is not negligible, which makes the device design difficult, and has a problem that manufacturing and assembly are difficult.

Furthermore, a human body cleaning device having an instantaneous heat exchanger has a configuration that makes it easy to reduce the size of the device because it does not have a large hot water storage tank like a hot water storage type, but on the other hand, the size of the blower Occupied a larger part in reducing the size of the entire apparatus.

In addition, if an air treatment device is installed to heat, cool, deodorize, chemically treat, or mix in diffusing substances such as fragrance, the area of contact between the treatment section and air must be ensured to reduce the size of the device. However, it is necessary to reduce the size. However, in this case, the pressure loss increases due to the decrease in the cross-sectional area of the channel at the contact portion, and the blower load increases due to the increase in the pressure loss. This imposes a further increase in size and high-speed operation of the blower, causing a deterioration in operability and workability and an increase in vibration noise. Had become contradictory.

Generally, an axial blower that is frequently used in the same manner as a centrifugal blower can obtain a large amount of air at a low pressure by using a small blower.

However, since a high pressure load such as a drying mechanism, a heating mechanism, a cooling mechanism and a deodorizing mechanism such as a honeycomb catalyst must be connected to a human body cleaning device or a toilet device, an axial blower is usually used. Sufficient ventilation performance without the required air volume Can't get

Disclosure of the invention

The present invention has been made to solve the above-mentioned problems. An object of the present invention is to provide a toilet device having a blower, which is excellent in operability, design, usability, and comfort even in a small toilet room, and furthermore, the device design. Another object of the present invention is to provide a toilet device that can be easily installed and constructed, and a method for designing the toilet device. That is, an object of the present invention is to provide a very small toilet apparatus by using a blower capable of obtaining a required air volume and pressure even at a low rotation and small size.

The invention according to claim 1 has been made to solve the above-mentioned problem.The invention relates to a toilet device having a blower driven and rotated by a motor,

The blower is

A suction port for sucking outside air,

An impeller support that is rotationally driven by a motor; and an outer periphery of the impeller support, which is arranged substantially evenly in the circumferential direction, and blows and boosts air sucked from the suction port by centrifugal force generated by rotation. An impeller having a blowing blade to perform;

With

The blower blades are configured as a speed-up cascade that increases the velocity of the air that has flowed in through the suction port and reduces the flow area by reducing the flow area in the radial direction from the center of the impeller support.

It is characterized by.

According to the first aspect, the air sucked from the suction port by the impeller of the centrifugal blower is blown and pressurized by the blower blade and is blown out. The blower blades use speed-increasing blades that reduce the flow area in the radial direction from the center of the impeller support. Can get You. Therefore, by attaching a small impeller blower to a human body local cleaning device or a toilet device, these can be reduced in size. In addition, since the blower can obtain a desired air volume even when it is rotated at a low speed, transmission of unpleasant vibrations during use can be prevented, and comfortable washing can be performed.

In claim 2, a pressure recovery means is provided on the outer periphery of the blower blade for converting dynamic pressure generated by rotation of the impeller into static pressure to recover the pressure. In this configuration, the pressure recovery means can be realized, for example, as a scroll casing integrally formed with a casing that rotatably supports the impeller.

In claim 3, when U _r is the radial velocity at the time of the impeller outflow, V _e is the rotational speed of the outer periphery of the impeller, and the flow coefficient Φ is defined as Φ = υ `` / ν _θ By setting the value to 0.15 or more, the size of the blower can be reduced to about half the size of the conventional type, and the toilet device can be significantly reduced in size. This makes it possible to reduce the size of the blower without increasing the number of revolutions, resulting in excellent comfort. This can be achieved by performing

In claim 4, the blower blades are configured such that a flow passage area formed between the adjacent speed increasing blades gradually decreases from an inlet portion to an outlet portion of the speed increasing blades. The configuration of the speed increasing blade can be suitably realized.

In claim 5, the blower blades are arranged such that the inclination of the chord connecting the leading edge of the inlet blade tip and the trailing edge of the outlet blade tip is in the same direction as the impeller rotation direction. The outflowing air can be effectively sent in the rotating direction, and a large pressure head and high air volume can be obtained.

According to claim 6, since air can be sent from a plurality of outlets, efficient air can be sent to a room or a human body even when used for air conditioning such as indoor heating and cooling. In claim 7, the discharge is performed by selecting a discharge direction by switching a plurality of discharge ports. Equipped with mouth-switching means so that air can be blown to the required place when needed, and to provide airflow with excellent comfort.Moreover, when a single blower is used for multiple purposes. Even if there is, it is possible to perform optimal ventilation without causing a decrease in air volume or a change in the number of revolutions.

In claim 8, a blower duct is provided which communicates with the blower and transports air from the blower to the discharge port. It is easy to handle and assemble, and the volume occupied by the air duct is small, and the entire device can be downsized.

In the ninth aspect, pressure recovery means for converting dynamic pressure into static pressure is provided at a connection portion between the blower pipe and the discharge port, so that air flowing at a high speed in the blower pipe having a small pipe cross-sectional area is provided. Ventilation is possible without losing pressure. If dynamic pressure is converted to static pressure, even if air is blown through a small-diameter air duct, the pressure required for air blowing is small and efficient air blowing is possible. As described above, if the required pressure can be reduced, the drive torque of the blower is also reduced, so that it is possible to drive with a small motor having a low rotation.

According to the tenth aspect, since a plurality of suction ports are provided, it is possible to perform optimal suction according to the application. For example, one of the suction ports is installed in the area around the bowl surface of the toilet bowl, which is a position where the odor can be efficiently sucked for deodorization, and the other suction port is used for air conditioning such as cooling and heating. For dry use, it can be installed on the back side where dust is not sucked or at a position away from the toilet.

Claim 11 includes suction port switching means for selecting a suction direction by switching a plurality of suction ports. This suction port switching means switches the suction port from a position where it is easy to suck odors to a position where it is difficult to suck odors so that unpleasant odors are not diffused during indoor air conditioning and drying. On the other hand, when deodorizing, switching to a position where the odor is easily sucked will enable effective deodorizing.

According to claim 12, by controlling the rotation speed of the blower, from the blower By providing the blower output adjusting means for adjusting the output state, even if the blower is also used for a plurality of purposes, it is possible to obtain a blowing amount according to the purpose. It is also possible to control the air flow according to room temperature and user preference. In particular, when a speed-increasing blade is used, it has excellent hydrodynamic characteristics and can obtain a large pressure head and a high airflow even at the same rotation speed, so it can be used in a wide range of applications from low airflow to high airflow. By controlling the number of rotations, it is possible to use a single blower.

In claim 13, since the output state of the blower is adjusted by the blower output adjusting means in conjunction with the discharge port switching means and / or the suction port switching means, the blowout load is switched by switching the discharge port and Z or the suction port. Even if the required airflow is different, it is possible to secure a suitable airflow for the application.

In Claims 14, 15, 16, 16, 18, and 20, since the air treatment device is provided in the pipeline communicating with the blower, a ring having high and low temperature, high humidity, odor, etc. Even in a toilet room where boundaries are not good, it can always be kept in a comfortable state. In addition, it is not necessary to increase the size of the blower or increase the number of revolutions even if the load on the blower increases due to the downsizing of these air treatment devices. It is possible to achieve both.

In claim 17, the air temperature adjusting means controls the temperature of the air based on the output of the air temperature detecting means, so that the air can be blown at an optimum temperature suitable for the application.

In claim 19, since the air whose temperature has been adjusted by the air temperature adjusting means is used as the local drying means after the local washing, it is possible to maintain a comfortable state by drying the moisture after the local washing. it can.

Claims 21 and 22 include an air processing unit control unit that starts, stops, and adjusts the output of the air processing unit in conjunction with the discharge port switching unit and / or the suction port switching unit. , Even if the odor component concentration is different Alternatively, it is possible to perform air treatment that is optimal according to the user's preference and according to the application.

In claim 23, the blower includes a casing that rotatably supports the impeller, and is detachably attached to the casing and is detachably attached thereto, so that air blown out from the blower blades is directed to the outside. It is composed of a blowing duct to guide. According to this aspect, since the blower is sufficiently small and the blowing capacity can be freely controlled by controlling the rotation speed in a wide range, it is possible to replace only the blowing duct according to the application and operating conditions. In addition, there is no need to newly design the impeller support or the blower blades, or to change the arrangement and the layout, so that the number of parts can be reduced.

In claim 24, since the impeller support and the blower blades are configured with units having the same shape, it is not necessary to individually design a new unit, and a common unit can be used. Therefore, the number of parts can be reduced.

In claim 25, the motor is a DC brushless motor including a rotor having a permanent magnet, and an electromagnet arranged to face the rotor. The motor for rotating the blower is not particularly limited, but its operation and effect can be enhanced by using a DC brushless motor that is small but has a large rated output. In other words, the DC brushless motor can control the number of rotations freely, and can reduce the vibration and reduce the size even when used at high speed for a long time, so that the arrangement and the blowing capacity can be controlled freely. Furthermore, when a type of motor having an outer rotor is used as the DC brushless motor, the permanent magnets are arranged in the outer rotor, so that the permanent magnet can have a large magnet area and be small in size. However, a large rated output can be obtained, further enhancing the effect. In this way, the use of a DC brushless motor reduces the volume compared to the case of using an AC induction motor, so that it can be easily installed in a narrow space like a human body washing device. . Further, since the motor can be miniaturized in this way, its driving circuit can be easily incorporated. Claim 26 relates to the second invention,

In a method for designing a toilet device including a blower that is driven and rotated by a motor, the blower includes:

A suction port for sucking outside air,

With

The blower blades are composed of a speed-up cascade in which the flow area is narrowed in the radial direction from the center of the rotating support to increase the velocity of the air flowing in from the suction port and flow out, and the flow coefficient Φ is reduced. This is the design method of the toilet equipment set to 0.15 or more as defined by the following equation.

= υ _Γ / ν _θ

However, U is the radial velocity at outlet of the blower, V _e refers to the rotational speed of the outer periphery of the rotary support.

In claim 26, the impeller of the blower is constituted by a speed increasing blade, and in claim 27, the flow coefficient φ of the blower is determined so as to be 0.15 or more. Since the method of designing the storage device has been shown, the size of the storage device can be significantly reduced.

BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a perspective view showing a blower unit for drying used in a human body local cleaning device.

FIG. 2 is a perspective view showing a configuration around an impeller of the blower.

FIG. 3 is a perspective view showing the blower with the blower duct of FIG. 1 removed.

FIG. 4 is a perspective view showing a conventional impeller. FIG. 5 is an explanatory diagram for explaining a circular blade of a conventional impeller.

FIG. 6 is an explanatory diagram for explaining the speed increasing blade used in the blower according to the present embodiment.

FIG. 7 is a graph showing a change in the cross-sectional area of the passage between the blades.

FIG. 8 is an explanatory diagram showing a speed triangle representing a state at the time of the outflow of the impeller.

FIG. 9 is an explanatory view of an impeller used in the blower unit shown in FIG.

FIG. 10 is an explanatory diagram for explaining the shape of the speed increasing blade.

FIG. 11 is a graph showing the measurement results of the hydrodynamic characteristics of the blower shown in FIG.

FIG. 12 is an external view of a drying fan unit.

FIG. 13 is a perspective view showing the internal structure of the blower.

FIG. 14 is a schematic diagram of a drying fan unit using a conventional arc blade.

FIG. 15 is a graph illustrating the measurement results of the hydrodynamic characteristics.

FIG. 16 is an explanatory view for explaining a pressure recovery means according to a second embodiment of the present invention. _C FIG. 17 is a block diagram for explaining a blowing mechanism using the pressure recovery means shown in FIG.

FIG. 18 is an explanatory diagram showing a blower control routine.

FIG. 19 is an explanatory view showing the internal structure of a conventional human body cleaning apparatus. <FIG. 20 is an external view of a conventional human body cleaning apparatus.

BEST MODE FOR CARRYING OUT THE INVENTION

DESCRIPTION OF THE PREFERRED EMBODIMENTS A human body local cleaning device as a toilet device according to a first embodiment of the present invention will be described <FIG. 1 is a perspective view showing a drying fan unit used for a human body local cleaning device < The blower unit 10 for drying includes a drive motor 12, a blower 14, and a blower duct 19. The blower 14 is attached to the drive shaft of the motor 12, sucks air from the suction port 14 a with the drive of the motor 12, and after increasing the pressure to a desired pressure, the blower duct 19 To send to.

A blower (not shown) is provided in the blower opening 19 a at the tip of the blower duct 19. The damper is self-closing when no air is blown to prevent backflow of sewage and garbage from the outside. On the other hand, when air is blown, the damper is automatically opened by the air pressure to blow air.

Further, the air duct 19 is provided with a heater for the purpose of raising the temperature of the drying air (not shown) and increasing the drying efficiency. The heater is controlled by a blast temperature control means for controlling the temperature to a predetermined value and drying safely and comfortably. That is, the blower temperature controller controls the temperature of the blown air by controlling the power supplied to the heater based on a detection signal from a temperature sensor provided in the blower duct 19.

Here, the suction port 14a of the blower 14 is configured as a single suction with only the motor mounting surface and the opposite surface due to the connection.However, if the configuration is such that cooling of the motor is performed at the same time, It may be arranged on the mounting surface side, or if it is desired to improve the characteristics at the time of high air flow, it may be a double suction structure that suctions from both surfaces.

FIG. 2 is a perspective view showing a configuration around the impeller 15 of the blower 14. In FIG. 2, the blower 14 includes an impeller 15 driven to rotate by a motor 12 and a scroll casing 18 (see FIG. 1). The impeller 15 includes an impeller support 16 fixed to the rotating shaft of the motor 12, and a high-speed blade 17 fixed substantially evenly in the circumferential direction of the impeller support 16. I have. The impeller support 16 is provided with a wing fixing ring 16a in the circumferential direction to prevent deformation of the wing due to rotation, thereby preventing unnecessary vibration of the wing and the like due to rotation. In the center of the impeller support 16, —Motor housing 16b is provided for mounting with the evening 12 inserted into the inner diameter part, and the overall size of the blower 14 is reduced. The upper portion of the motor housing 16b is a rectifying portion 16c which is rounded to reduce the air inflow resistance due to the protrusion of the motor 12.

Figure 3 on the outer peripheral side of the _c impeller support 1 6 is a perspective view showing the blower 1 4 removed the air duct 1 9 of Figure 1, scroll one Luque one single 1 8 through a mount 1 8 a is Are located. The scroll casing 18 has a spiral shape and functions as pressure recovery means for converting the dynamic pressure of the fluid flowing out while rotating from the impeller 15 into static pressure. Since the blower 14 can be used not only for drying but also for other purposes, the blower port 19a may be connected to another device, for example, a deodorizing device.

FIG. 4 is a perspective view showing a conventional impeller 100. The impeller 100 includes an impeller support 101 and arc-shaped blades 102 arranged at equal intervals on the outer periphery of the impeller support 101. As shown in FIG. 5, the arc blade 102 has an arc shape, and includes a blade front portion 102 a that is a blade tip of an impeller inflow portion and a blade that is a blade tip of an impeller outflow portion. The trailing edge 102b is connected with an arc-shaped wing. The air that has flowed into the impeller 100 is bent in the same direction as the rotational direction represented by the arrow in FIG. 5 as it flows from the leading wing portion 102 a to the trailing edge portion 102 b. Outflow from the impeller 100. The circle shown in Fig. 5 indicates the size of the cross-sectional area of the flow path between the blades formed by adjacent blades, and the size of the circle changes almost during inflow and outflow. This indicates that the cross-sectional area of the flow channel is almost constant.

FIG. 6 is an explanatory diagram for explaining the speed increasing blades 17 used in the blower 14 according to the present embodiment. The speed-increasing wing 17 has a shape in which the inclination of the chord represented by a straight line connecting the leading edge 17 a and the trailing edge 17 b is the same as the rotation direction indicated by the arrow. is there. When the air flowing through the speed-increasing wing 17 enters the wing leading edge 17a, it is bent in the same direction as the rotational direction, and flows out along the wing trailing portion 17b. The circle shown in FIG. 6 is drawn so that the adjacent speed increasing blades 17 are in contact with each other, and indicates the cross-sectional area of the flow path. As can be seen from this circle, the size of the circle decreases from the leading edge〗 7 a of the blade to the trailing edge 17 b of the wing.In other words, the flow area becomes smaller toward the downstream side, and the flow velocity decreases. It can be seen that the structure is increasing.

FIG. 7 is a graph showing a flow path cross-sectional area along a movement locus 0 L at the center of the circle in FIG. The arc blade 102 according to the prior art shown in FIG. Here, the length of the trajectory from the blade inlet to an arbitrary position is defined as the length of the trajectory from the blade inlet to the position corresponding to the blade tip. Let S be the area of the tangent circle, and S i be the cross-section of a circle whose diameter is the line connecting the two adjacent wing leading edges 17a.

In FIG. 7, the conventional arc blade 102 has a substantially constant flow path cross-sectional area ratio in the region of LZL _w > 0.2, whereas the speed increasing blade 17 of the present embodiment has However, the flow rate decreases almost linearly, and the minimum flow path cross-sectional area ratio is about 0.5. Therefore, it can be seen that the average speed at the time of outflow of the blower 14 of this embodiment is about twice as large as the average speed at the time of inflow. In addition, for the circular arc blade 102 according to the conventional technology in FIG. 5, the flow path cross-sectional area ratio decreases in the range of 0 <LZL _w <0.2, but this is due to the flow contraction due to the blade thickness. Yes, the flow velocity at inflow and outflow is almost the same.

Next, the theoretical background of the blower performance when the speed-increasing wing 17 is used is described. FIG. 8 is an explanatory diagram showing a speed triangle representing a state at the time of the outflow of the impeller.

Here, the radial velocity at U "is the impeller outlet, circumferential relative speed when V ₂ is the impeller outlet, W ₂ is the relative velocity at the impeller outlet, the impeller inside diameter, R ₂ is the impeller outer diameter , Β ₂ represents the impeller exit angle.

Further, the flow rate Q, the impeller height H, an impeller rotational angular velocity omega, the rotational speed of the impeller periphery V _e, when the total pressure of the blower and P _t, flow coefficient: phi, pressure coefficient: Yuno It is expressed by the following equations (1) and (2).

Φ = U _r / V _e … (1) = P _t / {(p / 2) V _e ² } (2)

U _r and V _e are represented by the following equations, respectively.

U _r = Q / (2 π R ₂ H)

V R 2 ω

From the speed triangle at the exit of the impeller, it is transformed into the following equation.

U _r = W ₂ c 0 s (π-β ₂ )

V 2 = W ₂ si η (κ-β,)

Furthermore, assuming that the radial velocity at the impeller entrance is U _in

U, _n = Q / (2 π R, H)

= {ν _θ (2 TT R ₂ H)} / (2 KR, H)

= Φ V, (R ₂ / R

Here, if the area ratio of the speed increasing part is ζ

W ₂ = no ζ

U _r = {φ V _fl (R ₂ / R,) / ζ} si η (π-β ₂ )

V ₂ = {V, (R ₂ / R / ζ)} cos (π-β) If the absolute velocity in the circumferential direction of the blade outlet is V and the slip at the time of outflow is ignored, V is expressed by the following equation (Α) Is represented.

V = (V _e + V ₂ )

= V _e {1 + φ (R ₂ / R,) cos (π-β ₂ ) / ζ} ■■■ (A) As is clear from equation (Α), the rotational speed of the air flowing out of the impeller It is shown that は changes depending on the area ratio の of the speed-up portion, and the smaller the ζ, the higher the flow rate in the rotational direction. The work of such a centrifugal blower is due to the centrifugal force of rotation, so if the rotational speed at the time of outflow increases, the same effect as increasing the rotational speed can be obtained. Large pressure head and high air volume can be obtained. In other words, by using the speed-increasing wings 17, a large pressure head and a large air volume can be obtained even with a low rotation speed and a small impeller, and the equipment can be significantly downsized. Noh.

In general, if the fan is designed to have a high air volume, the size of the scroll casing installed to convert the dynamic pressure of the impeller into static pressure must be large. However, for the following reasons, according to the speed increasing wing 17, the scroll casing 18 can be reduced.

That is, if the flow coefficient φ ′ taking into account the speed increasing effect of the speed increasing blade 17 is defined as follows,

φ '= U _r / V

= φ / [{1 + (R ₂ / R)) cos (π-β ₂ ) / ζ}] φ は changes depending on the area ratio 速 of the speed increasing part, and 、 'decreases as ζ decreases You can see that.

The outflow angle α at this time is

= tan " ¹ ()

It can be seen that the smaller &, the smaller α. The optimal design condition of the blower is when the outflow angle and the divergence angle of the scroll casing match, so by using the blades with speed increasing effect, a large pressure head and high air volume can be obtained. However, since the spread angle of the optimal scrolling can be reduced while the air volume is high, the size of the entire blower can be reduced.

Further, the speed increasing blade 17 can reduce the flow coefficient (based on this, the impeller 15 itself can be realized. That is, the flow coefficient of the above equation (1) < It can be transformed into

Φ = u _r / v _e

= Q / (2 κ ₂ ² ω) ■ · ■ (3) As shown in equation (3), Φ is a dimensionless number, and is one index that indicates the operating conditions of the blower. Applying the similarity rules for blowers, different conditions The characteristics of a blower operated at a small size can be universally represented.

The flow rate Q as a device design variable is constant, and the impeller rotation speed N has an upper limit in order to prevent vibration and noise, so that it can be made almost constant. By transforming equation (3) as follows, equation (B) is obtained.

π R ₂ ² H = {Q / (2 ω)} ■ (1 /) ■■■ (Β) Here, the left side of the equation (を) represents the volume of the impeller. From the right side, it can be seen that the volume of this impeller is proportional to the reciprocal of the flow coefficient φ. In other words, if operation can be performed with a large flow coefficient Φ, the size of the impeller can be reduced, and the size of the blower can be reduced. Considering that the conventional blower is used at Φ = 0.06 to 0.09 (average: 0, 0 7 5), it can be operated at φ = 0.15 or more. Can be about half or less in size. If Φ = 0.18 or more, it is needless to say that the size can be reduced to half that of the smallest blower in the conventional technology.

As described above, the blower of the present embodiment can realize a blower having the same rated output with half the capacity of the conventional blower, so that the conventional blower that uses two blowers for drying and room heating is different from the conventional blower. One unit can be shared.

Furthermore, when switching the flow path, a new flow path switching mechanism is required, but there is no need to consider the reliability and size of this mechanism and the problems of pressure loss generated in the switching section. Since it can be arranged at any required position, there is no need to route the duct, and the entire unit can be reduced in size.

Further, the design of the blower unit can be made very simple. Furthermore, when switching the flow path, of course, it is not possible to use multiple applications simultaneously, but if the blower is provided independently, the necessary air can be blown at any time, so it has excellent comfort and usability. Things.

FIG. 9 is a schematic view of an impeller 15 used in the blower unit shown in FIG. Where impeller outer diameter: D ₂ = 56 mm, impeller inner diameter: D, = 47 mm, impeller Height: H = 8 mm and the number of blades is 36. The ratio of the inner diameter to the outer diameter of the impeller: λ is set to about 0.85. λ is determined in consideration of the following points. In other words, when λ is reduced, noise such as wind noise can be reduced, but the characteristics at high airflow deteriorate as the suction area of the blower decreases. On the other hand, when λ is increased, the characteristics at high airflow are slightly improved, but due to the shorter blade length, separation easily occurs inside the impeller, lowering efficiency and increasing noise. Taking these factors into consideration, λ is determined as a condition under which the characteristics at the time of high air volume and the characteristics such as noise can be compatible. In view of these points, λ is preferably 0.75 to 0.95, particularly preferably 0.8 to 0.92.

Figure 10 and Table 1 show the main specifications of the speed-up wing shape. The ratio の of the cross-sectional area of the channel in the speed increasing section can be set arbitrarily according to the blade shape. If ζ is small, a large speed can be obtained, so that a higher pressure and a higher air volume can be designed.However, if λ is too large, the speed distribution at the time of the outflow of the impeller becomes large, resulting in lower efficiency. The noise level also rises. If ζ is taken too large, the speed effect will be weakened and it will be difficult to improve the characteristics. Therefore, in consideration of these parameters, ζ is preferably 0.30 to 0.80, particularly preferably 0.4 to 0.65, and 本 is set to 0.45 in the present embodiment.

Table 1 Prior art product Invention product

Impeller outer diameter [mm] 66 59

Impeller inner diameter [mm] 5 1. 5 50

Impeller height [mm] 28 7. 8

Impeller volume [mm ³ ] 9.6 X 10 2. 1 X 10 ⁴ Flow coefficient [1] 0.065 0.26 Pressure coefficient [1] 1.35 1.30 Wing shape

Speed increase ratio [1] 0.9 0.94

Wing exit angle [deg] 1 55 1 65

Wing inlet angle [deg] 90. 0 87. 5

Scroll angle [degree] 3.5 4.0

Design conditions, flow rate: 0.30 mVmin, total pressure: 137.0 Pa Figure 11 shows the measurement results of the hydrodynamic characteristics of the blower unit shown in Figure 3. At the same time, when compared with the results of the conventional fan using arc blades, the pressure coefficient remains high until the flow coefficient Φ becomes very high. The results obtained by measuring performs actual blower designed using the impeller volume for the same design conditions as shown in Table 1, about 22% (2. 1 X 1 0 4 / 9. 6 X 1 0 ⁴⁾ can be miniaturized by Nima. Generally instantaneous type heat exchanger volume of 1 200 W about power used on the human private washing apparatus and Bok - directional device think about 9. ⁴ X 1 0 4 mm ³ der Rukoto, the conventional blower, It has a volume comparable to an instantaneous heat exchanger with only the impeller volume. Thus, the use of the blower according to the present invention makes it possible to reduce the size of the human body local cleaning device and the toilet device.

FIG. 12 is an external view of a blower unit for drying, and FIG. 13 is a perspective view showing the blower 14. As shown in FIG. 12, the blower 14 and the blower duct 19 are detachably connected to each other through a duct connection portion 19b. The blower 14 according to the present embodiment is extremely small and quiet, and can obtain a high air volume and a high pressure at a low rotation speed. Therefore, even if the blower shape is not designed for the air blow application, the blower 12 can be used. By simply adjusting the rotation speed, it is possible to handle a very wide range of applications, from high airflow applications for indoor air conditioning to low airflow applications for deodorization.

In other words, the blower 14 is used as a common part, and the load, blown area, duct length By adjusting the air flow and appropriately selecting and using a blow duct having a different shape, it is possible to use the blow duct as it is for different blow applications by changing only the shape of the blow duct. Therefore, if a small blower is used as a common part, it is not necessary to consider the blower performance and size as design variables when designing equipment and examining internal arrangements, and it is possible to flexibly respond to changes in design specifications. Yes, it is very easy to design a human body cleaning device and a toilet device.

Fig. 14 is a schematic diagram of a blower unit for drying using a conventional arc blade. <Fig. 15 is a schematic diagram of a fan unit using a conventional arc blade for drying and drying. 7 shows the measurement results of the hydrodynamic characteristics in the case of connecting. When a load is connected compared to a single blower, the characteristics are significantly reduced, and the flow coefficient at the design point is 0.065.

FIG. 16 shows an example of pressure recovery means according to the second embodiment of the present invention. The air supplied from the connection pipe connection port 22 having a smaller flow path cross-sectional area flows into the pressure recovery means 21. The pressure recovery means 21 is formed as a conduit that expands gradually to convert it to a blowing area and flow velocity suitable for the application, so that the air flowing at high speed is gradually decelerated as the cross-sectional area of the flow path increases. The air is sent to the air outlet 24 having a larger flow path cross-sectional area.

At this time, the large dynamic pressure of the high-speed air during the deceleration process is gradually converted into a static pressure, so that no pressure loss or energy loss occurs. Further, since the pressure recovery means 21 is divided into a plurality of passages by the partition walls 23, the deceleration can be efficiently performed, and the pressure can be sufficiently converted. Dividing the inside of the enlarged flow path in this way has a rectifying effect and prevents separation of the flow, so that pressure loss does not occur. If there is no pressure loss in this way, the load on the blower can be reduced, greatly contributing to downsizing and energy saving. In addition, by providing the pressure recovery means 21 with small energy loss, air can be transported through a pipeline having a smaller cross-sectional area than the air outlet. To reduce the size Always preferred.

FIG. 17 shows an embodiment in which an air blowing mechanism is configured by using the pressure recovery means 21 shown in FIG. The air supplied from the blower 14 is sent to the outlet switching means 33. The discharge port switching means 33 includes a heater 29 for heating the air as an air processing device, a temperature detection means 32 for detecting the temperature of the air, and a flow path switching means 31 for switching the flow path. The air switched by the flow path switching means 31 is guided to the air duct 28. The pressure recovery means 21 is connected to the air duct 28 at a position suitable for each application. The flow path switching means 31, the temperature detecting means 32, the heater 29 and the motor 122 are connected to the controller 30, and the controller 30 is activated when the user performs a remote control or manual operation. Then, control is performed such that a predetermined temperature, air volume, rotation speed, and air outlet are selected. In this embodiment, since the discharge port is provided with the pressure recovery means 21, even if air is blown through the blower pipe 28 having a smaller pipe diameter, pressure loss and energy loss are less generated, and the blower 14 and the motor 12 are It can be a small size suitable for a human body local cleaning device and a toilet device.

FIG. 18 is an explanatory diagram showing a transmitter control routine. In FIG. 18, the controller 30 controls the rotation speed of the blower 14 based on a predetermined program. That is, in step S12, it is determined based on an output signal from a switch (not shown) whether drying, deodorization, or heating is required, and any of the processing is requested. If there is no such process, the process is temporarily terminated. On the other hand, if any one of these processes is requested, the process proceeds to step S14. In step S14, the target rotation speed of the blower is calculated. The target rotation speed is obtained, for example, from a preset table or an arithmetic expression. In this case, for example, as the demand for drying, deodorizing, or heating increases, the rotation speed of the blower is set higher. In the following step S16, the detection value from the rotation speed sensor of the blower is read, and the process proceeds to step S18. In step S18, the detected value of the rotation speed sensor and the target The deviation from the target rotation speed is determined, and it is determined whether these deviations are within a predetermined range.If it is determined that the deviation is higher than the predetermined range, the process proceeds to step S20, and the control power to the blower is increased or decreased. You. In this way, the blower is controlled to a predetermined rotation speed based on a request for drying, heating, or the like. Note that the target rotation speed of the blower can be set so that it can be changed according to the user's preference.

In the embodiment of FIG. 17, the configuration using the heater 29 as the air processing device has been described. However, instead of the heater, a deodorizing device, a cooling device, or a device for radiating a diffused substance such as a fragrance may be provided. However, some can be combined. When several air conditioners are used in combination, it is desirable that the selection and output adjustment of the air treatment device be linked with the flow path switching means 31. In addition, since the air can be routed freely using a small-diameter air duct 28, the air-blowing unit 34 may be installed outside the human body local cleaning device and the tray device, or as an option. It may be retrofitted.

Here, only the configuration of the blower-side pipeline has been described, but it can be said that air can be sucked from the appropriate suction port by combining the flow path switching means and the blower pipeline for the suction-side pipeline. Not even. In particular, when air is cooled by a heat pump or the like, it is necessary to effectively discharge the waste heat accompanying the cooling out of the system in order to ensure comfort. Since the air can be effectively blown by the air duct having a small diameter, it is particularly suitable for the use of discharging such waste heat. Further, in this case, effective waste heat can be performed by providing a waste heat discharging means (not shown) outside the apparatus and connecting it to a blower unit.

FIG. 19 shows the internal structure of a conventional human body cleaning apparatus. Deodorizing blower unit 50, drying blower unit 51, washing nozzle 52, heating toilet seat 53, indoor heating blower unit 54, hot water sink 55, controller 56, flow control valve 57 It has been. FIG. 20 is an external view of a conventional human body cleaning apparatus.

The present invention is not limited to the above embodiment, and does not depart from the gist of the present invention. The present invention can be implemented in various modes within the scope, and for example, the following modifications are also possible.

(1) The hydrodynamic characteristics of the blower can be changed according to the application, and may be determined according to the design. For example, if the motor used can be reduced in size, the inner diameter of the impeller can be further reduced, so that the outer diameter of the impeller can also be reduced. Similarly, if the size is reduced as it is, the required pressure and air volume cannot be obtained, and the motor speed must be increased. Therefore, it is necessary to improve the hydrodynamic characteristics of the blower. For example, in order to further improve the characteristics at high airflow, it is necessary to use both suction, increase the scroll angle, increase the outflow angle at the blade outlet, and reduce the cross-sectional area ratio of the speed increasing section. They can be used, or they can be combined. By doing so, the flow coefficient ^ at the time of installation of the blower can be made larger than 0.26 shown in Table 1, and it is possible to experimentally exceed 0.4, and the pressure coefficient is 2 It has been confirmed that it is possible to set the value to more than 0.

(2) Toilet devices, such as toilets equipped with a function to dry local parts after washing, a deodorizing function, an indoor heating function, etc., as well as a human body cleaning device that sprays washing water to local parts of the human body, storage cabinets, etc. Is included. In this case, the toilet device incorporating the blower may be built in the device body in advance, or may be retrofitted.

(3) When scroll casing is used as the pressure recovery means, its shape is not particularly limited. For example, the following configuration can be adopted.

① Scroll shape drawn by logarithmic spiral

The shape of the scroll casing can be a logarithmic spiral represented by the following function in polar coordinates.

r = r _o exp [0 · tan Θ r]

r: Outer diameter of scroll casing

r _Q : Outer diameter of impeller Θ: Polar coordinate angle

Θ r: Angle of logarithmic spiral

② Scroll shape drawn by Archimedes spiral

The shape of the scroll casing can be an Archimedes spiral represented by the following function in polar coordinates.

r = r ₀ + C

r: Outer diameter of scroll casing

r. : Outer diameter of impeller

Θ: Polar coordinate angle

C: Constant

③ Wingless diffuser

In the above-described embodiment, the configuration using scroll casing is described. However, a wingless diffuser in which the entire periphery of the impeller is opened may be used without using scroll casing. In this configuration, when the air is uniformly pumped over the entire circumference of the impeller according to the rotation of the blower, dynamic pressure is naturally converted to static pressure as it spreads spirally. In the present embodiment, since air is blown over a wide range in the circumferential direction of the impeller, it is suitable for blowing air for heating a toilet room or blowing air after deodorization.

④ Wing diffuser

Further, a winged diffuser for converting dynamic pressure into static pressure may be arranged on the outer periphery of the impeller. This winged diffuser can be configured as an arc-shaped standing wall in the radial direction. Industrial applicability

INDUSTRIAL APPLICABILITY The present invention is applicable to a human body local cleaning device for cleaning a local part of a human body and a toilet device used for heating a toilet room.

Claims

The scope of the claims

1. In a toilet apparatus provided with a blower driven and rotated by a motor, the blower is

A suction port for sucking outside air,

An impeller support that is rotationally driven by the motor; and air that is blown from the suction port by centrifugal force generated by rotation, which is arranged on the outer periphery of the impeller support and is substantially even in the circumferential direction. An impeller having a blower blade for increasing pressure,

With

A toilet device characterized by the above-mentioned.

2. In Claim 1,

A toilet device, wherein pressure recovery means for recovering pressure by converting dynamic pressure generated by rotation of the impeller to static pressure is disposed on the outer periphery of the blower blade.

3. In a toilet device provided with a blower driven and rotated by a motor, the blower includes:

A suction port for sucking outside air,

An impeller support that is driven to rotate by a motor; An impeller having a blowing blade to perform;

With

-/ 'Toilet equipment with cucumber volume coefficient Φ set to 0.15 or more when Φ is defined by the following equation.

= υ _Γ / ν _θ However, U _r is the radial velocity, V _e at the outflow of the impeller means a rotational speed of the outer periphery of the impeller.

4. In any one of claims 1 to 3,

A toilet apparatus, wherein the blower wing is configured such that a flow passage area formed between the speed-increasing wing and an adjacent speed-increasing wing gradually decreases from an inflow portion to an outflow portion of the speed-increasing wing.

5. In any one of claims 1 to 4,

A toilet apparatus wherein the blower blades are arranged such that the inclination of a chord connecting a leading edge of an inlet-portion wing tip and a trailing edge of an outlet-portion wing tip is in the same direction as a rotation direction of an impeller.

6. In any one of claims 1 to 5,

A toilet device having a plurality of discharge ports for discharging air blown out from the impeller.

7. In Claim 6,

A toilet apparatus comprising: a discharge port switching unit that switches the plurality of discharge ports to select a discharge direction.

8. In any one of claims 1 to 5,

Equipped with a discharge port for discharging air ejected from the impeller,

A tilling device including a blower duct communicating with the discharge port and the blower to transport air from the blower to the discharge port, wherein a cross-sectional area of the blower pipe is smaller than a cross-sectional area of the blower of the discharge port. . 9. In Claim 8,

Pressure recovery means for converting dynamic pressure to static pressure at a connection portion between the blower pipe and the discharge port Toilet device equipped with.

10. In any one of claims 1 to 9,

A toilet device having a plurality of the suction ports.

1 1. In claim 10,

A toilet apparatus provided with suction port switching means for switching the plurality of suction ports to select a suction direction. 1 2. In any one of claims 1 to 11,

A toilet device having a blower output adjusting means for adjusting an output state from the blower by controlling a rotation speed of the blower.

1 3. In claim 7 or claim 11,

A toilet device comprising a blower output adjusting means for adjusting an output state from the blower by controlling the rotation speed of the blower in conjunction with the discharge port switching means and the Z or suction port switching means.

1 4. In any one of claims 1 to 13,

A toilet device provided with an air treatment device in a pipe communicating with the blower.

15. In claim 14,

The toilet device, wherein the air treatment device is configured by air temperature adjusting means for adjusting the temperature of the air.

1 6. In claim 15, The air temperature adjusting means includes heating means for heating the air by performing heat exchange to increase the temperature of the air, and cooling means for cooling the air by performing Z or heat exchange to reduce the temperature of the air. Toilet equipment.

1 7. In claim 16,

Air temperature detecting means for detecting the temperature of air in a conduit for guiding air flowing out of the blower,

The toilet device, wherein the air temperature adjusting means is configured to control the temperature of the air based on the output of the air temperature detecting means.

18. In any one of claims 15 to 17,

A toilet apparatus provided with air conditioning means for using the air, the temperature of which has been adjusted by the air temperature adjusting means, as cooling and heating of a toilet room.

1 9. In any one of claims 15 to 17,

Toilet equipment provided with a local drying means for using the air, the temperature of which has been adjusted by the air temperature adjusting means, as hot air for drying the moisture adhered to the human body part after the local washing.

20. In claim 14,

The above-mentioned air treatment device is a toilet device constituted by odor component removing means for adsorbing, decomposing or deteriorating odor components in the toilet room.

2 1. In Claim 7,

An air treatment device provided in a pipe communicating with the blower,

Start, stop and output adjustment of the air treatment device in conjunction with the discharge port switching means Air treatment device control means for performing;

Toilet device equipped with.

2 2. In claim 11,

An air treatment device provided in a pipe communicating with the blower,

Air treatment device control means for starting, stopping and adjusting the output of the air treatment device in conjunction with the suction port switching means;

Toilet device equipped with. 2 3. In claims 1 to 22,

The blower is

A casing that rotatably supports the impeller,

A blower duct which is detachably attached to the casing and which is detachably attached and guides air blown out from the blower blades to the outside;

A human body local cleaning device provided with:

2 4. In claims 1 to 23,

A toilet device equipped with multiple blowers composed of impellers of the same shape. 25. In claim 1 or claim 24,

A toilet device, wherein the motor is a direct current brushless motor including a rotor having a permanent magnet and an electromagnet arranged opposite to the rotor.

26. In the method of designing a toilet device equipped with a blower that is driven and rotated by a motor,

The blower is A suction port for sucking outside air,

With

The method for designing a toilet device, wherein the blower blades are configured as a speed-increasing cascade in which a flow area is narrowed in a radial direction from a center of a rotary support to increase a speed of air flowing in from a suction port and flow out. . 27. In the method of designing a toilet device equipped with a blower that is driven and rotated by a motor,

The blower is

A suction port for sucking outside air,

With

Design method for toilet equipment with a flow coefficient Φ set to 0.15 or more when Φ is defined by the following equation.

φ = υ _r / V _e

However, U _r is the radial velocity at outlet of the blower, V ₀ refers to the rotational speed of the outer periphery of the rotary support.