KR19990013939A - Dishwashing dryer - Google Patents

Abstract

Conventionally, the cleaning pump mounted in the washing machine has a problem that the pump capacity decreases even at a small intake air amount, resulting in a decrease in the cleaning performance.

The dish washing dryer of the present invention includes an impeller (10) having a first centrifugal blade (8) and a disc supporting the first centrifugal blade, a casing having an inlet and a discharge port in which the impeller 10 is embedded, and the impeller; The blade shape of the 1st centrifugal blade 8 is equipped with the electric motor which drives the, The rear blade 12 which set the inner periphery part about 90 degrees or less with respect to a predetermined rotation direction, and the outer periphery part, It has a front vane 13 whose angle is set to about 90 ° or more, and since liquid and gas can be pressurized with a simple configuration, and even water including bubbles can be pressurized and circulated, cleaning performance at the time of clogging the filter A dish washing dryer can be provided that realizes improvement, water saving, power saving, and time reduction.

Description

Dishwashing dryer

1 is a cross-sectional view of the dish washing dryer according to the first embodiment of the present invention;

2 is a view showing an impeller of a first embodiment of the present invention,

3 is a perspective view of an impeller of a second embodiment of the present invention,

4 is a perspective view of an impeller of a third embodiment of the present invention,

5 is a perspective view of an impeller of a third embodiment of the present invention,

6 is a view showing an impeller of Embodiment 1 of the present invention;

7 shows an impeller of a fourth embodiment of the present invention;

8 shows an impeller of a fifth embodiment of the present invention;

9 is a view showing an impeller of a second embodiment of the present invention;

10 is a view showing an impeller of a second embodiment of the present invention;

11 is a view showing a conventional dish washing dryer,

12 is a diagram showing the configuration of a centrifugal pump according to a sixth embodiment of the present invention;

Fig. 13 is a view showing the main part of the centrifugal pump according to the sixth embodiment of the present invention;

14 is a partially enlarged view of the runner of the sixth embodiment of the present invention;

Fig. 15 is a view showing the main part of the centrifugal pump according to the seventh embodiment of the present invention;

Fig. 16 is a view showing the main part of the centrifugal pump according to the eighth embodiment of the present invention;

17 is a view showing the main part of a centrifugal pump according to a ninth embodiment of the present invention;

18 is a sectional view of an essential part of a dish washing dryer according to a tenth embodiment of the present invention;

19 is a sectional view of principal parts of a cleaning pump according to a tenth embodiment of the present invention;

20 is a plan view of an impeller in a cleaning pump according to a tenth embodiment of the present invention;

21 is a sectional view of an impeller in a cleaning pump according to a tenth embodiment of the present invention;

Fig. 22 is a sectional view of another principal part of a cleaning pump according to a tenth embodiment of the present invention;

23 is a sectional view of principal parts of the dish washing dryer according to the eleventh embodiment of the present invention;

24 is a first time chart showing injection pressure in a tenth embodiment of the present invention;

25 is a second time chart showing injection pressure in a tenth embodiment of the present invention;

Fig. 26 is a time chart showing the operation of the washing pump in the twelfth embodiment of the present invention;

27 is a sectional view of an essential part of a dish washing dryer according to a thirteenth embodiment of the present invention;

28 is a sectional view of an essential part of a cleaning pump according to a thirteenth embodiment of the present invention;

29 is a sectional view of principal parts of a cleaning pump according to a thirteenth embodiment of the present invention;

30 is an essential part cross sectional view of the cleaning pump with shroud in the thirteenth embodiment of the present invention;

31 is an essential part cross sectional view of a cleaning pump according to a fourteenth embodiment of the present invention;

32 is an essential part cross sectional view of a cleaning pump according to a fifteenth embodiment of the present invention;

33 is an essential part cross sectional view of the cleaning pump in accordance with a sixteenth embodiment of the present invention;

34 is an essential part cross sectional view of the disc-shaped magnet coupling;

Explanation of symbols for main parts of the drawings

8: first centrifugal blade 10: impeller

12, 21, 32: front wing 13, 30: rear wing

33, 53, 63: washing pump 34: heater

55 cleaning nozzle 66 drain pump

67 blower

[Technical field to which the invention belongs and the prior art in that field]

The present invention relates to a dish washing dryer having a washing pump for pressurizing the washing water, and more particularly to a washing pump.

Hereinafter, the conventional dish washing dryer is demonstrated based on FIG.

In the case of washing dishes, the dishes are stored in the dish container 62 of the washing tank 61, the detergent is added and the operation is started. When the operation is started, first, a water supply step of supplying a predetermined amount of washing water to the washing tank 61 is performed so that the operation of pressing the washing water by the washing pump 63 is stabilized. The suction port and the water surface of the cleaning pump 63 have a substantially constant interval. Then, this washing | cleaning process which pressurized by the washing | cleaning pump 63 and heated by the heater 64 is sprayed from the washing | cleaning nozzle 65 with a detergent is performed. The washing water is sprayed in the vertical direction or the inclined upward direction from the spray hole of the washing nozzle 65. In addition, the cleaning nozzle 65 rotates substantially horizontally by this injection reaction force. In this way, the dishes are washed by the action of the collision force, the detergent, the heat, and the like of the washing water sprayed from the rotating washing nozzle 65.

After this washing | cleaning process of predetermined time, the washing | cleaning water containing the dirt wash | cleaned by the tableware etc. enters into the drainage process which discharges out of the dishwasher by the drain pump 66. Subsequently, a water supply step of newly supplying the washing water, a rinsing step of spraying the washing water from the washing nozzle 65 in order to rinse the dishes soiled by the detergent or the residue (the dirt attached to the tableware), and the The drainage process is repeated four times in succession to complete the cleaning process.

Subsequently, the blower 67 sends air outside the dishwasher into the washing tank 6l from the blower tube 68 to the washing tank 61 via the blower port 69, and operates the heater 64 intermittently to warm the air. The drying step of evaporating the water droplets affixed to the tableware by this warm air is performed. By this drying process, the humid air in the washing tank 61 is discharged out of the dish washing dryer from the exhaust port 70. Reference numeral 71 denotes a control device for controlling the operation of the washing pump 63, the heater 64 and the like. In addition, reference numeral 72 denotes an intake port for sending indoor air to the blower 67. Reference numeral 73 denotes a water supply valve for opening and closing the water supply path of the washing water. Reference numerals 74, 75 and 76 denote centrifugal vanes of the washing pump 63, the drain pump 66 and the blower 67, respectively, and reference numerals 77, 78 and 79 denote electric motors for driving them. Reference numeral 80 denotes a drainage path, and reference numeral 81 denotes a filter for recovering the residue.

In the conventional structure mentioned above, a washing | cleaning pump has the following subjects.

In general, the washing pump becomes incapable of pumping due to (1) the increase in air intake, (2) in the vicinity of the segment, even the slightest air becomes incapable of pumping, and (3) a large amount of air in the washing pump at start-up. In this case, the pump does not start normally. This operating characteristic is due to the phenomenon that the air inlet is blocked by the air and the water flow is interrupted.However, very little air does not flow out of the wing and accumulates because the water flow rate decreases and the pressure difference between the wing exit and the inlet increases. It is.

Therefore, in the dish washing dryer using such a washing pump, while being able to pressurize washing water stably, a certain amount or more of bubbles should not be mixed in the washing water to obtain washing ability. For example, when a general kitchen detergent is mixed, a large amount of foam is generated and the washing pump 33 cannot obtain the required pressing force. For this reason, a low foaming detergent which suppresses the generation of bubbles in the circulating washing water should be used. So-called `` dedicated detergent '' should be used.

In addition, when the filter is clogged, the amount of the washing water supplied to the washing pump decreases and the air is sucked in. However, in the case of a conventional pump, if the air is sucked at least, the pump capacity decreases and the washing performance is deteriorated. At this time, the cleaning pump causes pulsation, so that the cleaning pump discharge pressure periodically fluctuates greatly from almost zero to near the normal pressure. Therefore, noise is generated accordingly.

Moreover, the QH characteristic which shows the relationship between the flow rate Q and the discharge pressure H of the washing pump 53 is single, and in a washing | cleaning process, the washing water is sprayed from the washing | cleaning nozzle 55 by predetermined discharge pressure and flow volume. will be. For this reason, the circulation flow rate of the washing pump 53 is constant regardless of the quantity of dishes to be cleaned or the quality of the dirt, and the predetermined washing quantity and the depth of water at the suction portion of the washing pump 53 (the reference surface in the washing tank) Is called the "cleaning water level". In order to secure this washing | cleaning water quantity and washing | cleaning water level, it is necessary to control so that the quantity of washing water to be supplied and washing | cleaning water level will necessarily exist in a fixed range, and the water level detection means for it is required with high precision and high cost.

In addition, in order to obtain the predetermined | prescribed washing | cleaning performance in a washing | cleaning process, the predetermined | prescribed washing | cleaning water quantity should be heated with predetermined temperature to predetermined temperature. For this purpose, the heating capacity (also called a capacity) of the heater 34 needs to be large. In addition, the heating by the heater requires a long time, and the amount of use, power consumption, and operation time in the washing operation are related thereto.

[Technical problem to be achieved]

This invention solves the subject which the washing pump in the conventional washing machine mentioned above has.

[Configuration and Function of Invention]

The washing pump of the dish washing dryer of the present invention has a hybrid impeller having a rear wing at the inner circumference and a front wing at the outer circumference. The mixed phase impeller can easily circulate by pressurizing water containing gas, liquid, and air. Therefore, the cleaning performance in the case of foaming of the detergent described above or clogging of the filter is improved. It is also possible to pressurize the water, including the air, so that the level of the washing water can be lowered, which leads to savings in power required to warm water and warm water.

Invention of Claim 1 is equipped with the washing | cleaning tank which stores the to-be-cleansed object, the washing | cleaning means which has the injection hole which injects wash water, and the washing | cleaning pump which pressurizes wash water, The washing | cleaning pump is a 1st centrifugal vane, and An impeller in which a disc supporting a centrifugal blade is disposed, a casing having an inlet and an outlet for embedding the impeller, and an electric motor for driving the impeller, wherein the blade shape of the first centrifugal blade has a predetermined inner circumference. It has a rear wing which sets the exit angle to about 90 degrees or less with respect to the rotation direction, and the front wing which set the exit angle to about 90 degrees or more on the outer peripheral part, and the inner peripheral part and the outer peripheral part of a wing are connected in a curved shape. It is a dish washing dryer characterized by the above-mentioned.

According to the configuration of the present invention, the pressurization of the liquid is mainly performed by the action of the inner circumferential rear wing of the first centrifugal blade. In order to reduce the load torque caused by the rotation of the centrifugal blade and pressurize efficiently, the outlet angle is weakened. The turbo blade shape set to 90 degrees or less is used. The pressurization of the gas is performed by the action of the outer circumferential front wing of the first centrifugal blade having a siroco fan shape in which the exit angle is set to about 90 ° or more in order to obtain enormous air volume and wind speed. Therefore, the dish washing dryer which improved the drying efficiency can be provided by blowing air from a washing | cleaning means.

In addition, since the absolute velocity of the outflowing fluid is large, water and air, water mixed with bubbles, and even a large amount of air enters the pump, it is possible to quickly discharge the water or air to be retained in the casing, so that pumping is impossible. It does not fall into and can suppress extreme performance fall. That is, even when the filter clogging or the water supply amount is insufficient, the pump discharge pressure can be maintained at a higher pressure than the conventional pump.

Therefore, it can pressurize and discharge irrespective of the state of the fluid supplied to a washing | cleaning pump, and it aims at the improvement of the cleaning performance at the time of a filter clogging by the lack of water supply, the excess residue, etc., or the noise reduction, or for the low water supply cleaning. According to the present invention, there is provided a dish washing dryer which can reduce the amount of water used, shorten the operation time, and reduce the amount of power consumed. In particular, when blowing air, the inner circumferential rear wing of the first centrifugal wing serves as an inducer as an inlet guide vane for smooth air inflow. , Large air volume, and low input can be realized. And this means that the starting characteristic of a washing | cleaning pump can be improved significantly.

In addition, since the impeller of the present invention has a front wing having an exit angle of about 90 ° or more, the pump input tends to be slightly higher than that of a turbo impeller of a general rear wing, and compared with a turbo impeller, Rotate at low speed. Therefore, since the NZ noise generated in the impeller and the tongue is reduced, it is possible to provide a dish washing dryer having reduced noise during normal operation.

In addition to the invention of Claim 1, invention of Claim 2 sets the height of the wing of an outer peripheral part front wing to below the height of the wing of an inner peripheral part rear wing. Since the impeller of the present invention has an outer circumferential front wing configuration, the air discharge performance is certainly very excellent, but the pump input tends to be slightly higher for the rear wing of the same diameter. For this reason, a high input (high torque) type of cleaning pump drive motor is required.

According to this configuration, however, the input of the cleaning pump can be reduced without excessively lowering the air discharge performance. In other words, a smaller motor can be used, and a dish washing dryer can be provided in which the washing volume is increased due to the size of the washing mechanism or the size of the product is reduced.

In addition to the invention of Claim 1 or 2, invention of Claim 3 divides the outer periphery front wing into two directions substantially parallel to a disc, and some blades make an exit angle about 90 degrees or less, and an inner periphery part It is comprised from the 2nd rear wing which connected smoothly to the rear wing.

According to the present invention, in addition to the improved input characteristics in the invention according to claim 2, by extending the inner circumferential rear wing to the impeller outer diameter, a dish washing dryer having high cleaning performance with improved pump performance (flow rate, discharge pressure) is provided. Can provide.

In addition to the invention of Claim 3, invention of Claim 4 connects the said outer peripheral part front wing cross section and the wing cross section of a rear wing in substantially planar range in the range which does not discharge from an impeller outer periphery.

This configuration can separate the flow of the fluid between the outer circumferential front wing and the second rear wing of the first centrifugal blade, so that the flow of the fluid at the impeller outer circumference does not become disturbed. For this reason, the dish washing dryer which can improve the washing performance by the improvement of the pump performance by reducing a flow path loss, and the noise by the fluid disturbance can be provided.

In addition to the invention of Claim 1, invention of Claim 5 sets the exit angle of the outer periphery wing shape of a centrifugal blade to less than about 90 degrees.

According to the present invention, since the load on the impeller is reduced, the pump input can be reduced. Therefore, since a smaller pump driving motor can be used, it is possible to provide a dish washing dryer with low cost and small size.

In the invention according to claim 6, in the case of the invention of claim 1, the third centrifugal blade disposed between one or more blades of the first centrifugal blade has an inlet angle of about 90 with respect to a predetermined rotational direction. It has the rear wing which set the exit angle to about 90 degrees or less, and the front wing which set the exit angle to about 90 degrees or more on the outer peripheral part, The blade inner diameter of the said 3rd wing | blade is less than the 1st centrifugal blade inner diameter. It was enlarged.

By this structure, the fluid which flows between a 1st centrifugal blade and the front blade of an outer peripheral part can be rectified, and it can pass a flow path loss little.

As a result, the pump input can be reduced and the pump performance can be improved. In addition, since the inner diameter of the 3rd centrifugal blade is set so that it may become larger than the maximum diameter of the foreign material which passes through a filter, the foreign material does not become clogged in an impeller regarding the distance between the vanes of a wing entrance part becomes small.

As described above, according to the present invention, the pump driving motor is improved in addition to the improvement of the washing performance in both water saving, time reduction, and normal or clogged filter by improving the air discharge performance or the pump performance and reducing the pump input. It is possible to provide a dish washing dryer which realizes cost reduction and miniaturization by miniaturization.

In addition to the invention as described in any one of Claims 1-6, invention of Claim 7 sets the volume between the blades of an outer peripheral part front wing to equal or more than the volume between the wings of an inner peripheral part rear wing.

The impeller of the present invention is mainly composed of an inner circumferential rear wing for discharging washing water and an outer circumferential front wing for discharging water mixed with foam during air mixing out of the impeller. The discharge performance of the mixed water is improved by setting it equal to or larger than the volume between the wings of the housewife rear wing.

Therefore, it is possible to provide a dish washing dryer which aims at a higher water saving effect, a shorter operation time, a noise reduction when the filter is clogged, and an improvement in the cleaning performance.

In addition to the invention as described in any one of Claims 1-7, the invention of Claim 8 is equal to or more than the sum of the volume of the wing | blade of an outer peripheral part front wing, and the sum of the volume between the impeller suction part volume and the blade of an inner peripheral part rear wing. It is set to.

The impeller of the present invention is mainly composed of an inner circumferential rear wing for discharging washing water and an outer circumferential front wing for discharging water mixed with foam during air mixing, out of the impeller. By setting it equal to or more than the sum of the volume of the impeller suction portion and the volume between the wings of the inner circumferential rear wing, the discharge performance of the mixed water is dramatically improved.

Therefore, even when a high pressure washing pump is used, it is possible to provide a dish washing dryer which aims at a higher water saving effect, a shorter operation time, a noise reduction when the filter is clogged, and an improvement in the cleaning performance.

According to the ninth aspect of the present invention, a centrifugal pump is provided as a washing tank for storing a substance to be cleaned, a washing means having a jet port for injecting washing water, and a washing pump for pressurizing the washing water. A runner with a centrifugal vane disposed therein; a casing having an inlet and a discharge port incorporating the runner; and an electric motor for driving the runner; wherein the wing shape of the first centrifugal vane exits its inner portion with respect to a predetermined rotational direction. The rear wing shape with the angle set to about 90 ° or less, and the front wing shape with the exit angle set to about 90 ° or more on the outer side, and the inlet angle with respect to the predetermined direction of rotation between the first centrifugal blades. A second centrifugal shape having a substantially curved or straight forward wing shape having an exit angle of about 90 ° or more and an exit angle of about 90 ° or more and shorter than the wing height of the first centrifugal wing. It is a dish washer dryer equipped with a one or a plurality of disposed runners dog.

According to the structure of this invention, pressurization of a liquid is mainly performed in the rear wing shape part of a 1st centrifugal vane, and an exit angle is about 90 degrees or less in order to pressurize efficiently by making small load torque by rotation of a centrifugal vane. The so-called turbo blade shape set to is used. The pressurization of the gas rotates the front wing shape of the first centrifugal blade or the second centrifugal blade, which has a so-called siroak fan shape, in which the inlet angle and the outlet angle are set to about 90 ° or more in order to obtain enormous air volume and wind speed. Is executed.

In addition, since the absolute velocity of the outflowing fluid is large, water and air, which are mixed with bubbles, and even when a large amount of air enters the pump, can quickly discharge the water or air to be retained in the casing. It does not fall out and can suppress the extreme performance fall.

In particular, when the air is blown, in addition to the second centrifugal vane, the first centrifugal vane also rotates in a similar manner, and the first centrifugal vane serves as an induction guide vane that facilitates the inflow of air. As a result, a larger air volume can be realized than a general sirocco fan having the same diameter.

In addition, when discharging water, the fluid from the first centrifugal blade can flow out efficiently by the rectifying effect of the second centrifugal blade, and the pump efficiency is equal to or higher than that of a general turbo pump.

Thus, according to invention of Claim 9 of this invention, the fluid of all states, such as water, air, and water mixed with bubbles, can be pressurized and circulated. Here, the angle which the relative speed of the fluid in a blade | wing inlet part and an exit part makes, and the circumferential speed of a blade | wing is called an inlet angle and an outlet angle, respectively, according to the convention of a turbo fluid machine. In addition, the magnitude | size of an electric motor may be sufficient as long as an output enough to drive each load torque can be obtained.

In addition to the invention of Claim 9, invention of Claim 10 of this invention has a centrifugal pump which has a runner which connected the rear wing shape part and the front centrifugal shape part of a 1st centrifugal blade in a substantially smooth smooth shape. In the wing configuration of the invention according to claim 9, the direction in which the fluid flows between the rear wing shape and the front wing shape changes rapidly.

Therefore, in the present invention, by reducing the sudden change in the flow at this bending point, the generation of vortices can be prevented and the pump performance can be improved by reducing the passage loss between the wings.

In the case of the invention according to claim 9 or 10, in the case of the invention of claim 9 or 10, among the plurality of second centrifugal blades arranged between the first centrifugal blades, the first centrifugal position It has a centrifugal pump which set the inlet angle of the 2nd centrifugal blade facing a blade | wing to be larger than the inlet angle of another 2nd centrifugal blade.

In general, the centrifugal runner having a rear wing has a side that is not relative to the angle (flow angle of the fluid) of the absolute velocity vector of the flow in the vicinity of the blade on the side that energizes the fluid in the fluid at the wing exit outer peripheral portion. The angle of the absolute velocity vector up to the vicinity of the posterior wing is obvious when considering the velocity triangle of the fluid.

In the case of the blower, the flow fluid is mainly the air of the compressive fluid, so that the air collects at a position traveling in a predetermined rotational direction of the blade, so that when the inlet angle of the second centrifugal blade is adjusted to the angle of the absolute velocity vector obtained near the blade, It's okay.

However, when pressurizing water or the like which is an incompressible fluid, the angle of the absolute velocity vector of the fluid becomes larger as the inlet portion of the second centrifugal blade is in a more advanced position with respect to the predetermined rotational direction. The inlet angle of the wing must also be adjusted to it.

Therefore, according to the present invention, it is possible to reduce the passage loss of the blade especially when pressurizing an incompressible fluid such as water and to realize a pump with higher efficiency.

Invention of Claim 12 makes the internal diameter of the 2nd centrifugal blade which opposes a 1st centrifugal blade in the position which is late with respect to a predetermined rotation direction among the some 2nd centrifugal blade arrange | positioned between a 1st centrifugal blade, It is a centrifugal pump set larger than the inner diameter of a 2nd centrifugal blade.

In the invention according to claim 10, the front centrifugal blade shape portion and the front centrifugal blade shape portion of the first centrifugal blade are connected to each other in a smoothly curved shape, so that the radius of curvature of the first blade and the front wing shape portion of the first blade are substantially the same. The inter wing area between the second centrifugal vanes facing the wing is reduced. This causes this part to cause a new passage pressure loss, which causes a decrease in pump performance and noise generation due to the generation of vortices and the reduction of the effective passage area.

However, according to the configuration of the present invention, the second centrifugal blade ensures an effective inlet area, whereby the fluid flows more smoothly in the passage between the blades, and a high efficiency and low noise pump can be realized.

According to the invention described in claim 13, the distance between the first centrifugal blade and the second centrifugal vane at a position opposite to each other in a predetermined rotation direction from the first centrifugal vane is the distance between the second centrifugal vanes or the second centrifugal vane. It has a centrifugal pump set larger than the distance between the blades with the 1st centrifugal vane which exists in the opposing position earlier with respect to a predetermined rotation direction.

In particular, in the case of a pump configuration that receives large flow water (for example, when the runner rotation speed is high, when the runner outer diameter is large, etc.), the water flowing between the blades is additionally added to the water as an incompressible fluid. Due to the centrifugal force, it is biased toward the side of the blade in the direction of rotation. This is also the same when blowing.

Therefore, in the present invention, the passage area between the first centrifugal vane and the second centrifugal vane on the front side in the rotational direction is made larger than the other passage areas, thereby securing a passage area through which large flow water flows, Even when a large flow rate is pressurized, a pump having a large flow rate and a high efficiency can be realized without causing a flow path loss.

Invention of Claim 14 is equipped with the washing tank which accommodates the to-be-cleaned object, the washing | cleaning nozzle which has the injection hole which injects wash water, and the washing | cleaning pump which pressurizes wash water by the impeller driven by an electric motor, The impeller of a washing pump is provided. By installing a plurality of inner blades each independent of the center of rotation, and a plurality of outer blades independent of the center of rotation, the air is mixed with the washing water by the washing process to the washing pump. When it loses, air flows quickly to the outer periphery of the impeller because the absolute velocity of the fluid flowing out of the outer wing is high. For this reason, the inner blade is filled with washing water having a small mixing ratio of air, and can pressurize the washing water. The air and the washing water can be sent to the washing nozzle so that the washing water is sprayed by the washing nozzle and the rotation can be normally performed.

According to the invention of claim 15, the inner blade is inclined to the rear with respect to the predetermined direction of rotation of the impeller, the outer wing is forward shape with respect to the predetermined rotation direction of the impeller so that the fluid easily flows out from the outermost peripheral portion of the impeller It is formed to have a part. Thereby, the air in the washing water can be sent to the outer periphery of the impeller, and the washing water can be efficiently sent to the washing nozzle. Therefore, it is effective to carry out normal rotation of the impeller.

Moreover, the invention of Claim 16 makes the number of wings of an impeller more outer blade numbers than the number of inner blades. Thereby, the discharge flow volume of air becomes large and it can discharge air in a short time.

For this reason, air is easy to enter, such as when the number of washing water to be supplied is set less than that of a general centrifugal pump, or when the residue is collected in the filter at the same time as the washing process proceeds, and there are few openings through which the washing water passes. Even in the state, it is possible to pressurize and circulate the washing water by the impeller. That is, the washing operation can be performed while the washing water is reduced and the heat capacity of the dishes and washing water is smaller. Therefore, even with the same heating capability, the washing water can be heated to a predetermined temperature in a short time, and the predetermined washing performance and drying performance can be obtained.

Moreover, in invention of Claim 17, the outside wing which comprises a part of outer wing has larger distance to the inner surface of the casing incorporating an impeller than the outside wing and inner wing, and the outside wing has an inner side Since it is disposed in the gap between the outer blades on the extension of the gap between the blades, the gap of the outer blades is always a certain size or more between the casing inner surface of the cleaning pump from the inlet to the outlet. That is, even if a solid substance of a predetermined size or less enters the washing pump, it can be easily discharged to the outside of the washing pump without being blocked by the outer blade of the impeller, and the pressurizing capacity of the washing pump is stable for a long time.

In addition, the invention according to claim 18 is provided with a forward and reverse reversal means of an electric motor, and the strength or weakness of the injection pressure of the cleaning nozzle is selected between the respective steps of the cleaning step or the respective steps from the rotational direction of the impeller of the cleaning pump. By setting up the control apparatus which alternately switches inside, and wash | cleans the to-be-cleaned object, the motor is inverted and operated in a washing | cleaning process, and the shape of the outer blade of an impeller is switched forward and backward by the rotation direction. In the front, the absolute velocity of the fluid is high, and the pressurizing capacity of the cleaning pump is high. In contrast, at the rear, the absolute velocity of the fluid is small, and the pressurizing capacity of the cleaning pump is low. In this way, the pressurization capacity of the cleaning pump is largely switched. In other words, the injection pressure of the cleaning nozzle can be adjusted with strength and weakness. By providing the control device which can select this between each process, it is equipped with both the strong cleaning power which can wash | clean the completely stuck dirt, and the standard cleaning power which can wash normal dirt.

In addition, by providing a control device that alternately rotates the motor in a predetermined rotational direction and reverse rotation in each step, the pressure of the washing pump is increased without increasing the amount of washing water, and the spray pressure of the washing nozzle is temporarily increased. Since it can be made high, the water-saving high pressure washing | cleaning can be performed.

The invention described in claim 19 further provides a control device for driving the impeller of the cleaning pump in a reverse rotation direction with a predetermined rotation direction when the washing water is below a predetermined temperature in the washing step. By installing a control device for driving the impeller of the cleaning pump in a reverse rotational direction with a predetermined rotational direction, when the number of cleaning waters is lower than a predetermined temperature in the cleaning process, the impeller of the cleaning pump is driven in the reverse rotational direction to reduce the pressurizing capacity of the cleaning pump. do. That is, the blowing force of the cleaning nozzle can be weakened to reduce the cleaning noise.

Then, the soil is swelled while the object to be cleaned and the washing water are heated. In addition, when the washing water reaches a predetermined temperature or more, dirt can be washed by driving the impeller of the washing pump in a predetermined rotational direction to return the pressurizing capacity of the washing pump to a standard state. This makes most of the driving time lower than the standard operating noise.

In addition, the invention described in claim 20 is provided with a drain pump for discharging the washing water out of the dish washing dryer, and provides a control device for driving the impeller of the washing pump in the reverse rotation direction in the draining step, thereby operating the drain pump in the draining step. In parallel with this, the impeller of the washing pump is driven in the reverse rotation direction, and the washing water is drained out of the dish washing dryer while spraying the washing water from the washing nozzle to the object to be cleaned.

Therefore, while rinsing the dirt attached to the tableware and stirring the dirt having a low specific gravity contained in the washing water, it can be discharged out of the dish washing dryer together with the washing water by the drainage pump from the bottom of the washing tank. In addition, since the impeller is reversely rotating in the drainage step, since the inner blade acts as the front blade, the washing water can be pressurized by a small load.

Invention of Claim 21 is provided with the washing tank which stores the to-be-cleaned object, the washing means which has the injection hole which injects wash water, the filter which isolate | separates the dirt in washing | cleaning, and the washing pump which pressurizes wash water, Is provided with a first centrifugal blade driven by an electric motor, and a second centrifugal blade having a larger outer diameter than the first centrifugal blade in a substantially concentric circle, having a built-in centrifugal blade and a casing having a suction port and a discharge port. And a magnetic body that transmits torque to positions where the first and second centrifugal blades face each other.

In the present invention, a magnetic material (hereinafter referred to as a magnet coupling) is provided in both the first centrifugal blade and the second centrifugal blade to perform torque transmission between the two blades, thereby changing the mixing ratio of the washing water and air supplied to the cleaning pump. According to the (pump load), the rotational speed of the second centrifugal blade along the first centrifugal blade can be changed steplessly. That is, in addition to the two fluids, the blowing of air for discharging the washing water and the blowing of air for drying, the discharge of the mixed phase in which air and water are mixed is realized by one pump and a small electric motor.

Therefore, according to the present invention, since it can pressurize and discharge irrespective of the state of the fluid supplied to the pump, it is possible to prevent deterioration of cleaning performance due to insufficient water supply or excessive residue, or to reduce the amount of water used by low water supply cleaning. A dish washing machine can be provided that realizes reduction, shortening of washing time, and expansion of tableware capacity. Moreover, the dishwasher which improved the drying efficiency can be provided by blowing air from a washing | cleaning means.

The invention according to claim 22, in addition to the invention according to claim 21, has a wing shape of the second centrifugal blade having a straight or approximately curved front wing shape having an exit angle of about 90 ° or more. Even if it is mixed, the dishwasher which fully functions can be provided.

In the invention according to claim 23, in the invention according to claim 22, the blade shape of the first centrifugal blade has a straight or substantially curved rear blade shape in which the inner part is set at an exit angle of about 90 ° or less with respect to a predetermined rotational direction. It is a dish washer to have.

According to the present invention, the pressurization of the washing water is mainly performed by the first centrifugal blade having a rear wing shape, and the motor can be miniaturized by reducing the load torque, thereby increasing the height of the washing mechanism part composed of the washing means and the washing pump. It can be made small. Therefore, the dish washing volume can be enlarged without changing a product height. In addition, since the pump capacity can be quickly restored even when air is mixed during the cleaning, it is possible to provide a tableware that can always obtain stable cleaning performance.

In the invention according to claim 24, in the case of the invention according to any one of claims 21 to 23, the blade height of the second centrifugal blade is made higher than the blade height of the first centrifugal blade. It is.

According to the present invention, since the second centrifugal blade rotates during cleaning, the fluid which is about to return to the center portion of the impeller returns by the suction force of the second centrifugal blade and can suppress the occurrence of the secondary flow. Therefore, miniaturization and cost reduction of the pump can be realized by improving the efficiency. As described above, according to the present invention, it is possible to provide a dish washing machine which can reduce the pump input due to the efficiency of the pump, reduce the size, and reduce the cost, thereby increasing the volume of the dish washing volume and saving energy.

In the invention according to claim 25, in the case of the invention according to any one of claims 21 to 24, the difference between the outer diameters of the first centrifugal blade and the second centrifugal blade is set to be equal to or larger than the maximum diameter of the dirt passing through the filter. It is a dish washer characterized by the above-mentioned.

In the present invention, the gap between the first centrifugal vane and the second centrifugal vane is made larger than the maximum diameter of the remnant passing through the filter, so that even if solids such as broken pieces of tableware enter the pump, the first centrifugal vane and the second centrifugal vane It does not fall into the clearance of a centrifugal blade, and does not restrict a pump.

Therefore, according to the present invention, it is possible to provide a dish washing machine capable of obtaining stable washing performance by securing high reliability against entry of foreign matters.

Invention of Claim 26 made the number of the blades of a 2nd centrifugal blade more than the number of wings of a 1st centrifugal blade, The dish washer characterized by the above-mentioned.

In the present invention, the pressurization characteristic required in each step as a washing pump can be obtained by a smaller electric motor by reducing the efficiency drop caused by the rotational speed difference between the first centrifugal blade and the second centrifugal blade at the time of pressurizing the washing water. have.

Therefore, according to this invention, the dishwasher which achieves predetermined washing | cleaning performance and drying performance by a compact and low cost structure is implement | achieved.

According to the invention described in claim 27, in addition to the invention according to any one of claims 21 to 26, the torque of the electric motor 6 required to rotate the first centrifugal blade 1 at the time of pressurizing the washing water is T1, By setting the torque of the electric motor 6 required to rotate the second centrifugal blade 2 at the time of air pressurization to be T1 and the disassembling torque between the magnetic bodies to T3, so that the pump has a small torque capacity, even if the pump has a small torque capacity. This large second centrifugal blade can be rotated so that, when less washing water is supplied, even if air is sucked into the cleaning pump, the air which is about to stay in the casing by the second centrifugal blade having a large absolute velocity of the outflowing fluid is discharged. By the operation of discharging, the first centrifugal blade can pressurize the washing water, and when the washing water is sufficient, the rotation of the second centrifugal blade is separated, and only by the rotation of the first centrifugal blade. It can be carried out information.

Example

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described, referring drawings.

(Example 1)

Fig. 1 is an overall view of the dish washing dryer of the present embodiment, in which reference numeral 1 denotes a washing tank, reference numeral 2 denotes washing means having a jet port 3 for spraying washing water, and reference numeral 4 denotes a cleaning. A filter for separating water contamination, reference numeral 5 is a washing pump for pressurizing the washing water. Reference numeral 6 is a suction port for supplying the washing water to the washing pump, and reference numeral 7 is a discharge port for introducing the washing water into the washing means 2. In addition, as shown in FIG. 2, in the washing pump 5, the impeller 10 which arrange | positioned the 1st centrifugal blade 8 and the disc 9 which supports the 1st centrifugal blade 8 is contained. There is a casing 11, and the blade shape of the first centrifugal blade 8 sets the inner circumference of the inlet angle α1 to about 90 ° or less with respect to a predetermined rotational direction, and the outlet angle β1 to about 90 degrees. The rear wing 12 set below or less, and the front wing 13 which set the inlet angle (alpha) 2 to about 90 degrees or less, and the exit angle (beta) 2 to about 90 degrees or more on the outer peripheral part, The inner circumference and the outer circumference of the wing are connected in a curved shape. In addition, the first centrifugal blade 8 is fixed to the output shaft of the electric motor 14. The angle of the inlet angle α2 of the outer circumferential front wing 13 can be obtained by the following effects even if the inner circumferential portion and the outer circumferential portion of the blade are approximately curved at about 90 degrees or more.

As a basic characteristic, when the front wing 13 rotates in the clockwise direction, even if the circumferential speed at the time of rotation of the centrifugal blade is the same, the exit angle is set to 90 ° or more. It is characterized by the fact that the absolute velocity of the fluid increases.

On the other hand, the rear wing 12 of the first centrifugal blade 8 has an exit angle β1 of 90 ° or less when the direction of rotation is clockwise, so that the circumferential speed at the time of rotation of the centrifugal blade is the same. Since the absolute velocity of the fluid is small, the velocity head can be converted into the pressure head with little loss, and the liquid pressing force can be efficiently obtained.

Here, the angle which the relative speed of the fluid in a blade | wing inlet part and an exit part and the circumferential speed of a blade | wing makes is called an inlet angle and an outlet angle, respectively according to the convention of a turbo fluid machine. In addition, the magnitude | size of an electric motor should just be a thing which can acquire the output enough to drive each load torque.

Next, the operation of the cleaning pump 5 will be described. First, the impeller 10 which has the 1st centrifugal blade 8 is rotated clockwise by the electric motor 8. Water guided from the suction port 6 to the casing 11 is pressurized by the impeller 10 and discharged from the discharge port 7. Moreover, also in pressurization of air, when the 1st centrifugal blade 8 is rotated clockwise by the electric motor 8, since it is pressurized mainly by the rear blade 12, it can be used also as a blower. In particular, when blowing air, the rear wing 2 of the first centrifugal blade 8 functions as an inductor as an inlet guide vane that facilitates the inflow of air, so that there is more air volume than a normal sirocco fan of the same diameter, Low input and high efficiency can be realized.

Therefore, as a liquid containing gas, for example, when water containing bubbles is supplied to the washing pump 9, or when a large amount of air is present inside the casing 11 at startup, these fluids can be used as conventional washing pumps. The operation under the condition that cannot be cycled will be described. First, a case where a large amount of air is present inside the casing 11 is assumed. At this time, immediately after the rotation of the electric motor 8 is started, the cleaning pump 5 is in a low discharge capacity state with a large amount of air present in the rear blades 2.

By the way, the air which exists in the rear blade | wing 2 is rapidly sucked in by the discharge | emission performance by the front blade | wing 13, and is discharged | emitted out of the casing 11. By this operation | movement, air is removed from the rotation area | region of the 1st centrifugal vane 8, the periphery of the 1st centrifugal vane 8 is filled with water, and it returns to the normal operation state which pressurizes water.

In the middle of the operation, the residue left in the tableware is a phenomenon that occurs when the filter 13 is clogged by the filter 13, but in the conventional pump, the cleaning pump pulsates according to the degree of air content, thereby discharging the cleaning pump. The pressure periodically fluctuates significantly from nearly zero to near normal pressure. Therefore, the cleaning performance is significantly lowered, and noise is generated even in the cleaning pump.

However, according to the impeller of the present invention, even if a large amount of bubbles are mixed in the pump 5, the washing pump 9 can secure a stable pump pressure because the same operation can be quickly discharged out of the pump. It is to maintain the cleaning performance.

In particular, in the case where a large amount of air is present in the casing 11 and there is little water, the self-sufficiency effect that the pressurization capacity as a pump can be obtained immediately after operation by the above-described operation is the washing pump 5 of the present invention. Is unique).

Moreover, since the performance as a blower is also high and air can be injected from a washing | cleaning means toward a tableware by rotating a washing | cleaning pump at the time of drying, it can be used also as a drying blower.

As described above, according to the present invention, it is possible to pressurize and discharge irrespective of the state of the fluid supplied to the washing pump, to prevent deterioration of the cleaning performance due to insufficient water supply or excessive residue, and to reduce the amount of water used by low water supply cleaning. A dish washing dryer can be provided that realizes reduction, reduction of operating time, and reduction of power consumption. Moreover, the dish washing dryer which improved the drying efficiency by the blowing from the washing | cleaning means can be provided. Moreover, since it rotates at a lower speed than a turbo impeller compared with the impeller of the same diameter, NZ sound which generate | occur | produces in an impeller and a tongue part can be reduced, and a dish washing dryer with less noise can be provided.

In addition, as shown in FIG. 6, when the front wing 12 has the wing shape part 15 which recessed with respect to a predetermined rotation direction, and set the exit angle (beta) 2 to less than about 90 degrees, an impeller Since the load on (10) is further reduced, the pump input can be greatly reduced. In addition, the air discharge performance is somewhat lowered. However, when the induction motor is used for the driving motor, the impeller rotation is increased, so that the degree of reduction is minimized.

In addition, since a smaller motor for driving a pump can be used, a dish washing dryer can be provided that realizes low cost and small size. In addition, when the exit angle β2 of the front wing 12 is less than about 90 ° with respect to the wing shape, in the present embodiment, the front wing is defined as a curve in FIG. However, regarding the shape definition of the front wing or the rear wing, or the connection point of the front wing and the rear wing, when defining the shape by a straight line, a single curve, a compound curve, or a compound of a curve and a straight line can be considered. In such a case, some shapes may have a secondary flow or loss in a hydrodynamic manner, but of course they are shapes that can sufficiently exhibit the effects of the present invention.

In addition, although the impeller was demonstrated in the open wing structure in this Example, the effect | equivalent or more than this invention can be acquired also in the closed wing which installed the shroud.

(Example 2)

Since the basic structure is the same as that of Example 1, the characteristic structure in Example 2 is demonstrated using FIG. In the impeller 20 of this embodiment, the wing height H1 of the outer circumferential front wing 21 is set equal to or less than the wing height H2 of the inner circumferential rear wing 22.

As the wing shape where the wing height changes, as shown in Figs. 9 and 10 in addition to Fig. 3, a shape for preventing the occurrence of vortices between the wings and the reduction of passage loss as shown in Figs. Can be considered

Since the basic operation is the same as that of the first embodiment, it is omitted here.

According to the analogy in hydrodynamics, the flow rate is proportional to the third square of the vane height, the pressure is proportional to the second square of the vane height, and the pump input is proportional to the fifth square of the vane height. Therefore, in particular, when the blade height H1 of the front blade 21, which is the main cause of the pump input rise, is lowered, the impeller rotation speed increases due to the decrease in the input and the load torque, thereby increasing the discharge pressure and the flow rate. In other words, the pump input can be significantly lowered with little deterioration in air discharge performance or capacity. Accordingly, a smaller motor can be used, and a dish washing dryer can be provided in which the washing volume is increased due to the miniaturization of the washing machine unit or the size of the product is realized.

In addition, although the impeller was demonstrated by the open wing | blade structure in this Example, of course, the effect equivalent to or more than this invention can be acquired also in the closed wing | blade provided with the shroud. In addition, regarding the shape definition of a front wing, a back wing, or the connection point of a front wing and a back wing, when defining a shape with a straight line, a single curve, a compound curve, or a compound of a curve and a straight line can be considered. In such a case, there are also shapes in which the secondary flow and loss are hydrodynamically accompanied by the shape, but of course, the shape can sufficiently exhibit the effects in the present invention.

(Example 3)

Since the basic configuration is the same as that of the first embodiment, only the characteristic configuration of the third embodiment will be described with reference to FIG. 4. The outer circumferential front wing 32 is divided into two in a direction substantially parallel to the disc 31, and the wing at the lower side in the vertical direction has an exit angle β3 of about 90 ° or less and smoothly on the inner circumferential rear wing 30. It was set as the structure which has the 2nd rear wing | wing 35 connected closely. Moreover, the wing | blade of the upper direction of a perpendicular direction is set as the impeller 33 structure which makes the exit angle (beta) 4 the front blade | wing 32 of 90 degrees or more.

Since the basic operation is the same as that of the first embodiment, the description will be mainly given of the characteristic operation.

As a problem by setting the outlet angle of the impeller 33 to 90 degrees or more, the fall of the pump pressure by the increase of a pump input and an increase of dynamic pressure can be considered. In particular, when the pump input is high, problems such as cooling and durability of the motor occur. Therefore, it is necessary to achieve both air discharge performance and pump performance without raising the motor input as much as possible.

By the way, according to the structure of this invention, reduction of a pump input and improvement of a pump performance can be implement | achieved by changing the wing shape part of a wing outer peripheral part from the front blade | wing 32 to the rear blade | wing 35. Moreover, when the 2nd rear wing 35 is provided in the disk 31 side, and it is set as the impeller 33 which installs the front wing 32 in the upper part, air discharge performance will not be reduced. This is because bubbles passing through the blades of the impeller 33 flow while rising to the upper part of the impeller. However, since the front blades 32 are disposed on the upper part, the air discharge performance can be sufficiently obtained.

With this configuration, in addition to maintaining the air discharge performance, in addition to the improved input characteristics in the invention as set forth in claim 2, the impeller efficiency is improved by providing the second rear blade 35 at the impeller outer periphery to improve the pump performance ( It is possible to provide a dish washing dryer having high cleaning performance with improved flow rate and discharge pressure.

In addition, although the structure of the impeller 33 which installs the front wing | blade 32 on the disc 31 side, and installs the 2nd rear wing | blade 35 in the side near the suction port of the impeller 33 is also considered, the impeller 33 is also considered. It is contemplated that the inlet 6 may be used when disposed below the impeller 33. In addition, when the impeller is used in the horizontal direction, it is considered that the positional relationship between the second rear blade 35 and the outer circumferential front blade 32 has no influence on the effect of the present invention.

In addition, as shown in FIG. 5, the cross section of the front blade | wing 32 and the cross section of the 2nd rear blade | wing 35 are connected in substantially plane 34 in the range which does not protrude more than the outer periphery of the impeller 33. As shown in FIG. Thereby, the fluid flow between the front blade | wing 32 and the rear blade | wing 35 can be isolate | separated, and the fluid disturbance in the outer peripheral part of the impeller 33 can be reduced significantly. For this reason, reduction of a flow path loss and pump performance can be improved. In addition, by configuring the cross section of the front wing 32 and the cross section of the second rear wing 35 in the substantially flat 34, the mechanical strength of the front wing 32 and the second rear wing 35 can be improved. . Therefore, the thickness of a wing for improving wing strength can be made thin and weight reduction can be attained. Moreover, since an inexpensive material can be used for an impeller, cost reduction of an impeller can be aimed at.

In addition, it is possible to prevent noise caused by fluid disturbances. Therefore, the dish washing dryer with high washing performance which reduced the noise by the washing pump can be provided.

In addition, although the impeller was demonstrated in the open wing structure in this Example, the effect similar to this invention or more can also be acquired also in the closed wing provided with the shroud. In addition, regarding the shape definition of the front wing, the back wing, or the connection point of a front wing and a back wing, when defining a shape by a straight line, a single curve, a compound curve, or a compound of a curve and a straight line can be considered. In such a case, some shapes may be hydrodynamically accompanied by secondary flow or loss, but of course, they are shapes that can sufficiently exhibit the effects of the present invention.

(Example 4)

Since the basic structure is the same as that of Example 1, the characteristic structure in Example 4 is demonstrated using FIG. One or more third centrifugal vanes 41 disposed between the vanes of the first centrifugal vanes 40 have an inlet angle α3 of about 90 ° or less with respect to a predetermined rotational direction, and an exit angle ( It has the rear blade 42 which set (beta) 6 to about 90 degrees or less, and the front blade 43 which set the exit angle (beta) 7 to about 90 degrees or more on the outer peripheral part.

The blade inner diameter of the third blade is set to be larger than the blade inner diameter of the first centrifugal blade.

With this configuration, the fluid flowing between the first centrifugal blade and the front blade of the outer circumference can be rectified to allow passage of the passage loss to be small.

As a result, the pump input can be reduced and the pump performance can be improved. Naturally, since the air discharge performance is further improved, the amount of water supplied can be greatly reduced.

As described above, according to the present invention, the pump driving motor is improved in addition to the water saving, the time reduction, the cleaning performance at the time of normal operation or the clogging of the filter by the improvement of the air discharge performance or the pump performance and the reduction of the pump input. It is possible to provide a dish washing dryer with low cost and miniaturization due to miniaturization. In addition, since the inner diameter of the third centrifugal blade is set to be larger than the maximum diameter of the foreign matter passing through the filter, the foreign matter is not caught in the impeller.

In addition, although the impeller was demonstrated by the open wing | blade structure in this embodiment, of course, the effect equivalent to or more than this invention can be acquired also in the closed wing | blade provided with the shroud. In addition, regarding the shape definition of the front wing, the back wing, or the connection point of a front wing and a back wing, when defining a shape by a straight line, a single curve, a compound curve, or a compound of a curve and a straight line can be considered. In such a case, some shapes may be hydrodynamically accompanied by secondary flow or loss, but of course, they are shapes that can sufficiently exhibit the effects of the present invention.

(Example 5)

Since the basic structure is the same as that of Example 1, the characteristic structure in Example 5 is demonstrated using FIG.

The impeller 45 of the present embodiment is mainly composed of the inner circumferential rear wing 46 for discharging the washing water and the outer circumferential front wing 47 for discharging the water mixed with the bubble when the air is mixed out of the impeller 45, The inner diameter of the inner circumferential rear wing 46 or the outer circumferential front wing 47 so that the inter-blade volume 48 of the outer circumferential front wing 47 is equal to or greater than the inter-blade volume 49 of the inner circumferential rear wing 46, Outer diameter or wing height is set.

Next, the operation of the present embodiment will be described. Bubbles entering the pump are first expanded rapidly by negative pressure at the impeller inlet 50. In that state, it passes through the inter-blade flow path 51 of the inner peripheral part rear wing 46, and passes through the inter-blade flow path 52 of the outer peripheral part front wing 47 which has a higher absolute speed, and discharges it out of a pump from the discharge port of a pump. do. In this case, if the air releasing capacity of the outer circumferential front wing 47 is not higher than the washing water suction ability of the inner circumferential rear wing 46, it is not possible to discharge the rinsed water mixed with bubbles continuously, but the present invention provides an air releasing performance. Since the wing volume 48 of the high outer circumferential front wing 47 is made larger than the wing volume 49 of the inner circumferential rear wing 46, it stays in the inter-blade flow path 51 of the inner circumferential rear wing 46. Air can be released early.

Therefore, it is possible to provide a dish washing dryer which further reduces the water-saving effect, the shortening of the operation time, the reduction of the noise when the filter is clogged, and the improvement of the cleaning performance.

In addition, when the inter-wing volume 48 of the outer circumferential front wing is set equal to or larger than the sum of the impeller suction volume 53 and the inter-wing volume of the inner circumferential rear wing 49, the wing volume of the outer circumferential front wing is set. It can enlarge and it can make air discharge performance from an impeller higher. In particular, when the washing pump is used at high pressure or the washing water is used at high temperature, the air sucked into the impeller expands rapidly. In order to secure the discharge performance of the pump, it is necessary to discharge this air at an early stage.

By the way, according to this structure, even if the air filled in the whole impeller is taken in, sufficient discharge performance can be ensured.

(Example 6)

12 and 13, reference numeral 101 denotes a first centrifugal wing 104 having a rear wing shape 102 and a front wing shape 103 extending outward from the center thereof, and a front wing shape. A runner having a second centrifugal vane 105 having a reference numeral 106 is a casing having a suction port 107 and a discharge port 108 of the fluid. The wing shape of the first centrifugal blade 104 is formed from the outer periphery of the runner 101 toward the center, first of which is formed a front wing shape 103 which is curved to have a convex portion in the opposite direction to the rotation direction, and then curved to protrude toward the rotation direction side. The rear wing shape part 102 which was formed is formed. Reference numeral 109 denotes an electric motor for driving these centrifugal vanes, and the casing 106 draws fluid from the container main body 106a incorporating the runner 101 and the output shaft portion of the motor 109 inside the casing 106. It is formed of the container cover 106c which has the axial sealing member 106b to seal. The first centrifugal blade 104 and the second centrifugal blade 105 are fixed to the output shaft of the electric motor 109, so that the two centrifugal blades rotate in the same manner. It is comprised as the centrifugal pump 110 which pressurizes a liquid and gas as these main components.

In addition, as shown in FIG. 14, when the rotation direction is made clockwise, the rear wing shape part 102 of the 1st centrifugal vane 104 may make the inlet angle (alpha) 1 and the exit angle (beta) 1 about 90 degrees or less. The so-called turbo blade shape set to is used. In addition, the inlet angle (alpha) 2 and the outlet angle (beta) 2 of the front wing shape part 103 have what is called a sirocco fan shape set to about 90 degrees or more. On the other hand, the inlet angle α3 and the outlet angle β3 of the second centrifugal blade 105 have a sirocco fan shape set to about 90 ° or more. As a basic characteristic, when the direction of rotation of the second centrifugal blade 105 is clockwise, even if the circumferential speed at the time of rotation of the centrifugal blade is the same, the absolute velocity of the fluid is large due to the relationship of the velocity triangle of the outlet, Suction power can be obtained. Therefore, compared with the 1st centrifugal blade 104, there exists a suction force more than the outer diameter is large and the circumferential speed is large.

On the other hand, when the rear wing shape portion 102 of the first centrifugal blade 104 has the rotational direction clockwise, the outlet angle β1 is 90 ° or less, so that even if the circumferential speed at the time of rotation of the centrifugal blade is the same, Since the absolute speed is small, the speed head can be converted into the pressure head with little loss, and the liquid pressing force can be efficiently obtained.

Next, the operation of the centrifugal pump 110 will be described.

First, the runner 101 having the first centrifugal blade 104 and the second centrifugal blade 105 is rotated clockwise by the electric motor 109. Water guided from the suction port 107 to the casing 106 is pressurized by the respective centrifugal blades and discharged from the discharge port 108. Moreover, also in pressurization of air, the electric motor 109 rotates the 1st centrifugal blade 104 and the 2nd centrifugal blade 105 clockwise. Then, it pressurizes mainly by the 2nd centrifugal blade 105, and can be used also as a blower. In particular, when blowing air, in addition to the front wing shape part 103 of the 1st centrifugal blade 101 or the 2nd centrifugal blade 105, although the 1st centrifugal blade 101 rotates similarly, this 1st Since the rear wing shape 102 of the centrifugal blade 101 functions as an inductor as an inlet guide blade which facilitates the inflow of air, it is possible to realize more air volume than a normal sirocco fan of the same diameter.

Therefore, as a liquid containing a gas, for example, when a water containing bubbles is supplied to the centrifugal pump 110, or when a large amount of air is present inside the casing 106 at the time of startup, these centrifugal pumps may be used. The operation under the condition in which the fluid cannot be circulated will be described.

First, a case where a large amount of air is present inside the casing 106 is assumed. At this time, the first centrifugal blade 104 and the second centrifugal blade 105 are rotated clockwise by the electric motor 109. Immediately after the start of rotation of the electric motor 109, the second centrifugal blade 105 only stirs the water in the casing 106 with a large amount of air present in the first centrifugal blade 104. Do not discharge

By the way, the suction speed of the second centrifugal vane 105 with a large absolute velocity of the fluid flowing out from the second centrifugal vane 105 stays inside the casing 106, in particular in the rotational region of the first centrifugal vane 104. The operation of discharging bubbles and air outwards is made within a short time. By this operation | movement, air is removed from the rotation area | region of the 1st centrifugal blade 104, the periphery of the 1st centrifugal blade 104 can be filled with water, and water can be pressurized. As a result, air existing in the casing 106 is extruded, and water is discharged from the discharge port 108 via the second centrifugal blade 105.

In addition, even if a large amount of bubbles are mixed again during the operation, the state in which the pump can be stably pumped by the same operation is maintained. In this way, water containing bubbles can be pressurized or circulated.

In particular, in the case where a large amount of air is present in the casing 106 and there is little water, the self-sufficiency effect that the pressurization capacity as a pump can be obtained immediately after operation by the operation described above is unique to the centrifugal pump of the present invention.

In addition, when the water is discharged, the fluid from the first centrifugal blade can be efficiently discharged by the rectifying effect of the second centrifugal blade, and the pump efficiency is equal to or higher than that of a general turbo pump.

Thus, according to this invention, the centrifugal pump which can pressurize and circulate the fluid of all states of water, air, and water mixed with the bubble can be provided. Moreover, the magnitude | size of an electric motor should just be a thing which can acquire the output enough to drive each load torque. Moreover, the centrifugal pump for a washing | cleaning machine exhibits the following effects.

First, it is possible to use a high foaming detergent. Second, even if the level of the washing fluctuates due to some factor and the water becomes low and a small amount, it functions as a washing pump. That is, as the dishwasher, it is possible to provide a dishwasher capable of realizing energy savings and resource savings due to the reduction of the amount of water used and the reduction of the temperature rise time. Third, since the cleaning nozzle for discharging the washing water to the tableware can also be used as a drying fan for injecting the drying air used to dry the tableware, it is possible to realize the miniaturization and cost reduction of the mechanism part by eliminating the dry fan unit used separately. .

(Example 7)

Since the basic structure is the same as that of Example 6, the characteristic structure in Example 7 is demonstrated. In FIG. 15, the rear wing shape 102 and the front wing shape 103 of the runner 101 are connected in a smooth curved shape 111. Moreover, of the 2nd centrifugal vanes 105 arrange | positioned between the 1st centrifugal vanes 104, the 2nd centrifugal vanes which oppose the 1st centrifugal vanes 104 at the position later with respect to a predetermined rotation direction ( The inner diameter of 112 is set to be larger than the inner diameter of the other second centrifugal blade 105.

Since the basic operation is the same as that of the first embodiment, the description will be mainly given of the characteristic operation.

First, a part of the air or water that enters through the inlet 107 of the runner 101 presses the passage between the wings along the rear wing 102, and then the front wing 103 and the second centrifugal. The flow velocity is further increased by passing between the blades 105, and finally discharged from the discharge port 108. At this time, since the rear wing 102 and the front wing 103 are connected in a smooth curved shape 111, the fluid flowing along the wing flows more smoothly, so that It does not cause generation and increase of passage loss.

Moreover, the inner diameter of the 2nd centrifugal blade 112 is enlarged with respect to the other 2nd centrifugal blade 105, and the area | region between the wings of the said substantially curved-shaped part 111 and the 2nd centrifugal blade 112 is fully secured. Therefore, the fluid can flow more smoothly from the first centrifugal blade 104 to the second centrifugal blade 112. In addition, at the time of blowing, it acts efficiently as a low noise fan.

Therefore, in the present embodiment, the generation of vortices and the passage loss between the wings are reduced by reducing the sudden change in the flow at this bending point and sufficiently securing the flow path area between the wings of the first and second centrifugal blades. It is possible to provide a pump which is capable of improving the pump performance and reducing the noise due to the reduction of the pressure.

Moreover, the centrifugal pump for a washing | cleaning machine exhibits the following effects.

First, it is possible to use a high foaming detergent. Secondly, even if the washing water level is changed by some factor so that the water becomes low and small, it functions as a washing pump. Third, since the cleaning nozzle for discharging the washing water to the tableware can also be used as a low noise drying fan for injecting the drying air used to dry the tableware, it is possible to realize the miniaturization and cost reduction of the mechanism part by eliminating the dry fan unit used separately. Can be.

(Example 8)

Since the basic structure is the same as that of Example 6, the characteristic structure of Example 8 is demonstrated. In FIG. 16, the second centrifugal which opposes the 1st centrifugal vane 104 in the position which was advanced with respect to a predetermined rotation direction among the some 2nd centrifugal vanes 105 arrange | positioned between the 1st centrifugal vanes 104. In FIG. The inlet angle alpha 4 of the blade 120 is set larger than the inlet angle alpha 3 of the other second centrifugal blade 5 to form a gentle inclination.

Since the basic operation is the same as that of the sixth embodiment, the description will be mainly given of the characteristic operation.

In general, a centrifugal runner having a rear wing is located in the fluid at the wing exit outer periphery, near the rear wing on the other side with respect to the angle of the absolute velocity vector of the flow near the wing on the side that energizes the fluid (outflow angle of the fluid). It becomes clear that the angle of the absolute velocity vector increases until considering the velocity triangle of the fluid.

In the case of the blower, since the flowing fluid is mainly the air of the compressive fluid, the air is collected at a position preceding the predetermined rotation direction of the blade, so that the inlet angle of the second centrifugal blade may be adjusted to the angle of the absolute velocity vector obtained near the blade.

However, when pressurizing water or the like which is an incompressible fluid, the angle of the absolute velocity vector of the fluid becomes larger as it is in a position further ahead of the predetermined rotational direction with respect to the inlet of the second centrifugal blade, so that the inlet of the second centrifugal blade is increased. The angle must also fit there.

Thus, the configuration of the present embodiment is such that the inlet angle α4 is horizontal to the streamlined direction of the fluid flowing into the second centrifugal vane 120 opposite to the first centrifugal vane 104 at a position advanced with respect to the predetermined rotational direction. ), The flow path resistance to the second centrifugal blade 120 can be reduced, and the rectifying effect can be maximized.

Therefore, according to the present invention, it is possible to reduce the passage loss of the blade, especially when pressurizing incompressibility such as water, to realize a pump with higher efficiency. Moreover, the centrifugal pump for a washing | cleaning machine exhibits the following effects.

First, it is possible to use a high foaming detergent. Second, even if the level of the washing fluctuates due to some factor and the water becomes low and a small amount, it functions as a washing pump. Third, since the cleaning nozzle for discharging the washing water to the table can also be used as a drying fan for injecting the drying air used to dry the table, the machine can be miniaturized and the cost can be reduced by eliminating the dry fan unit that was used separately. .

(Example 9)

Since the basic structure is the same as that of Example 6, the characteristic structure of Example 9 is demonstrated. In FIG. 17, the inter-blade distance 121 between the first centrifugal blade 104 and the second centrifugal blade 105 in a position opposite to each other in the predetermined rotation direction from the first centrifugal blade 104 is The distance 123 between the second centrifugal vanes 105 or the distance between the vanes 122 with the first centrifugal vanes 104 at a position opposite to each other in the predetermined rotation direction from the second centrifugal vanes 105 is greater than that. This is the set configuration.

In particular, in the case of a pump configuration that delivers a large flow of water (for example, when the runner rotation speed is high, when the outer diameter of the runner is large, etc.), even when the water is an incompressible fluid, the water flowing between the wings Due to the centrifugal force applied, it flows deflected to the front side with respect to the direction of rotation of the blade (this also applies to blowing).

Further, according to the configuration of the present embodiment, it is natural that the distance between the wings 122 and 123 (the first centrifugal blade and the second centrifugal blade in the opposite position later in the predetermined rotational direction than the first centrifugal blade) Between the blades of the 105 or between the second centrifugal blades 105 is narrower than the distance between the blades shown in the other embodiments, but as described above, the fluid between the blades in the centrifugal runner must be one-sided by the centrifugal force. The fluid must be deflected and ejected to the wing side, and a secondary flow such as swirl flow due to negative pressure is generated on the side ahead of the rotation direction.

By the way, in the structure of a present Example, since the distance between the wings of a 2nd wing is narrowed in this inter wing area | region, the effect of rectifying secondary flow is rather high, and efficiency improvement can be implement | achieved.

As described above, the present embodiment makes the effective passage area in the second centrifugal blade larger by making the interpass wing area between the first centrifugal blade and the second centrifugal blade closer to the rotational direction than the other passage area. It is possible to provide a pump for increasing the securing and rectifying effect, improving the performance and reducing the noise.

In addition, the centrifugal pump for a washing machine exhibits the following effects.

First, it is possible to use a high foaming detergent. Second, even if the water level is changed due to some factor and the water level is low and small, it functions as a cleaning pump. Third, since it is also possible to use a washing nozzle for discharging the washing water into the dish as a drying fan having a large amount of air to spray the drying air used for dish drying, it is possible to reduce the size of the mechanism part and reduce the cost by eliminating the drying fan unit used separately. Can be realized.

(Example 10)

18 is a general view of the dish washing dryer of the present embodiment.

18 and 19, reference numeral 201 denotes a washing tank, reference numeral 202 denotes a dish container for storing objects to be cleaned, such as dishes and cooking utensils, and reference numeral 203 denotes a washing to pressurize the washing water. The pump, reference numeral 204, is an impeller of the cleaning pump 203, and reference numeral 205 is an electric motor for driving the impeller 204. Reference numeral 206 denotes a heater for heating the washing water, reference numeral 207 denotes a washing nozzle having an injection hole for spraying the washing water, and reference numeral 208 denotes a drain pump for discharging the washing water out of the dishwasher. Reference numeral 209 denotes a control device for controlling the operation of the cleaning pump, the heater 206 and the like.

Here, in particular, the impeller 204 has a rear inner blade 204a having an exit angle set to 90 ° or less with respect to a predetermined rotational direction on the inside with respect to the rotation center, as shown in FIG. 20, and an exit angle on the outside. It has a front outer blade 204b set to 90 degrees or more, and the number of wings of the impeller 204 is formed so that the number of outer blades may become larger than the number of inner blades 204a. That is, the outer wing 204b has the outer wing 204b-1 and the outer wing 204b-2, and has the outer wing 204b-2 in the middle of the outer wing 204b-1.

21, the outer blade 204b is formed at least at a height of at least two, so that the outer blade 204b-1 and the outer blade 204b-2 of the height H2 are at the height H1. It consists of). And so that the outer side wings 204b-1 may not adjoin, it arrange | positions as shown in FIG.

Next, the operation as the dish washing machine of the present embodiment will be described. Since the operation in the washing step is basically the same as the conventional one, the description is omitted. The characteristic operation in this embodiment is the operation of the washing pump 203 in the washing step.

In the washing step, as the process proceeds, the residue is accumulated in the filter, so that the washing water cannot be supplied to the washing pump 203. Therefore, by the suction force of the washing pump 203, the washing water is sent to the washing pump 203 in a state where air is mixed. At this time, since the absolute velocity of the fluid flowing out of the outer blade 204b is large, air is sent to the outer peripheral portion of the impeller 204.

Therefore, the inner blade 204a of the impeller 204 is filled with washing water with a small mixing ratio of air, and can pressurize the washing water. The air and the washing water can be sent to the washing nozzle 207, and sprayed from the washing nozzle 207 and the rotation is normally performed. In addition, since the number of wings of the impeller 204 is arrange | positioned so that the total number of the outer side wing | wing 204b-1 and the small side wing | wing 204b-2 which become an outer blade | wing may become larger than the number of the inner side wing | wing 204a, Discharge flow rate increases, and air can be discharged in a shorter time.

Thus, since the washing water in a state containing air can be pressurized and circulated by the impeller 204, the amount of washing water supplied in the washing step can be reduced in this embodiment as compared with a general centrifugal pump. have. Therefore, the heat capacity of the washing water and the dishware becomes small, and even if the heating capacity of the heater 206 is the same, it can be heated to a predetermined temperature in a short time.

In addition, when the filter is not mounted correctly in the cleaning process, foreign matters having a predetermined size or less enough to pass through a second filter (not shown) that prevents foreign matters from entering the cleaning pump 203. . However, in the present embodiment, in the outer wing 204b having a large number of wings and a small gap, the outer wing 204b-1, which differs in wing height by height H1 and height H2, is separated from the outer wing 204b. -2), and the outer blades 204b-1 are arranged so as not to be adjacent to each other, the gap between the outer blades 204b can always obtain a predetermined size or more from the inlet to the outlet.

For this reason, even if the foreign material 204c enters the washing pump 203, the washing pump 203 is formed by the gap between the casing of the washing pump and the outer blade 204b of the impeller 204 as shown in FIG. 22. It is discharged to the outside, and there is no filter clogging by the foreign material 204c. For example, the foreign material 204c which has passed between the blade | wings of the inner blade 204a of the inlet part of the washing | cleaning pump 203 has the outer side blade | wing 204b-2 and the washing | cleaning pump 203 in the outer part of the impeller 204. It passes through the clearance gap formed in the inner surface 203a, and discharges it out of the washing | cleaning pump 203. Therefore, under various operating conditions, the pressurizing capacity of the cleaning pump 203 is stabilized.

In this way, the pressurizing capacity of the washing pump 203 is maintained as it is, and the water supply amount of the washing water can be reduced. Thereby, the heating time for raising the washing water to a predetermined temperature in the washing step or the heating rinsing step can be shortened by the same heating capacity. In other words, it is possible to achieve a predetermined cleaning performance and drying performance, but also to shorten the operating time of the water-saving and cleaning process and to save power.

In addition, in each step of the rinsing step performed by replacing the washing water according to the type and amount of the dirt, the pressurization capacity of the washing pump 203 is stabilized even if the washing water is reduced, so that the injection from the washing nozzle 207 is normally performed. It can be performed and the required rinsing effect can be obtained. Of course, this also shortens the time for heating rinsing and saves power.

In addition, in the drying process, the outside of the dish washing dryer is sent to the washing tank 201 by a blower (not shown), and the heater 206 is intermittently operated to produce warm air, which is attached to the tableware by the warm air. By evaporating the water droplets, the humid air in the washing tank 101 is discharged out of the dish washing dryer from an exhaust port (not shown). Therefore, in the present embodiment, if the control device 209 performs the heat rinsing step of the same operation time as before, the temperature of the dish and the attached water droplets can be higher than that of the conventional dish washer. Therefore, the drying speed of the to-be-cleaned object improves, and the improvement of drying performance and shortening of a drying time are aimed at. In this way, the whole operation time can be shortened including drying.

(Example 11)

In the present embodiment, the basic configuration is the same as that of the tenth embodiment, and the washing tank 201, the dish container 202, the washing pump 210, the impeller 204, the electric motor 205, the heater 206, the washing nozzle ( 207 and having a drain pump 208, the description of the basic configuration is omitted. As shown in FIG. 23, the washing | cleaning pump 210 is connected to the control apparatus 212 which controls operation | movement of the washing | cleaning pump 210, the heater 206, etc. by the forward / backward inverting means 211 of the electric motor 205. As shown in FIG. The direction of rotation is also controlled. In addition, the impeller 204 has a blade | wing similar to Example 1.

Then, the operation in the washing step will be described. In the present embodiment, in particular, by selecting and operating the rotational direction of the electric motor 205 in the washing step, the outer blades of the impeller 204 can be switched in the forward direction and the rearward direction, so that the pressurizing capacity of the cleaning pump 210 is large and small. You can switch to That is, as shown in FIG. 24, although it increases from the load W1 of the washing | cleaning pump 210 to the load W2, the pressurization capability increases and the injection pressure (P1) of the washing | cleaning nozzle 207 is injected ( P2) to act as a height. This makes it possible to select an appropriate cleaning power according to the amount and quality of the dirt.

Thus, by providing the control apparatus 212 which can select the injection force of the washing | cleaning nozzle 207 between each process, the strong cleaning power which can wash | clean the completely stuck dirt, and the standard cleaning power which can wash normal dirt are provided. The provided washing can be obtained by a single dish washing machine.

In addition, in each step of the cleaning step, the control device 212 alternately switches the electric motor 205 in a predetermined rotational direction and reverse rotation, thereby pressurizing the cleaning pump 210 without increasing the amount of the washing water. It is possible to increase the capability to temporarily increase the injection pressure of the cleaning nozzle 207.

That is, since the cleaning pump 210 restores the pressurization capacity in a short time to the mixing of air by the effect of the blades of the impeller 204, the circulation water is increased. It can operate without adding the water volume of washing | cleaning which supplies water, and the injection pressure of the washing | cleaning nozzle 207 can be raised like FIG.

In this regard, the means of adjusting the rotational speed by using a conventional centrifugal impeller to increase the pressurizing capacity is an effect that is difficult to obtain because it is necessary to increase the amount of washing water to be fed in conjunction with the amount of circulation. Therefore, conventionally, high pressure cleaning can be performed in a water-saving type, and it is possible to realize an improvement in cleaning power and a reduction in the amount of water used.

In addition, when the washing water is below a predetermined temperature in the washing step, the control device 212 mainly drives the impeller 204 of the washing pump 210 in the reverse rotation direction, thereby reducing the pressurization capacity of the washing pump 210. can do. Thereby, the injection force of the washing | cleaning nozzle 207 can be weakened, and the washing | cleaning noise by the collision or dripping of the washing | cleaning water to the washing tank 201 can be reduced. Then, the soil is swelled while the object to be cleaned and the washing water are heated.

After that, when the washing water reaches a predetermined temperature or more, the control device 212 mainly drives the impeller 204 of the washing pump 210 in a predetermined rotational direction, thereby increasing the pressurizing capacity of the washing pump 210 in a standard state. By returning to, the jetting force of the cleaning nozzle 207 can be increased to clean the dirt. In other words, it is possible to obtain a predetermined cleaning performance and to keep the operation noise of the cleaning process quiet most of the time.

(Example 12)

In the present embodiment, the basic configuration is the same as that of the eleventh embodiment, and the description of the basic configuration is omitted. As shown in FIG. 23, the cleaning pump 210 has a forward and reverse inverting means 211 and is controlled by the control device 212. Therefore, operation | movement of a drainage process is demonstrated.

At the same time as the drain pump 208 is operated in the drainage step, the washing pump 210 is operated as shown in FIG. 26. In this case, the inverse inverting means 211 rotates the electric motor in the reverse direction to the washing process. That is, the control apparatus 212 which drives the impeller 204 to reverse rotation with a predetermined rotation direction is provided.

In this way, by operating the washing pump 210 in a drainage step, the washing pump 208 drains the washing water from the washing nozzle 207 to the object to be cleaned while being drained by the drain pump 208. Then, while rinsing the dirt attached to the dishware and stirring the dirt having a light specific gravity contained in the washing water, it can be discharged out of the dish washing dryer by the drain pump 208 from the bottom of the washing tank 201.

In addition, in the conventional drainage process, the dirt having a low specific gravity floats on the upper surface of the washing water and is a strong dirt that tends to remain on the bottom even when drained from the bottom of the washing tank 1.

In the drainage step, since the impeller 204 is rotating in reverse, the inner blade acts as the front blade, so the washing water is pressurized with a small load. Therefore, as the amount of energization of the device, only a slight addition of the washing pump 210 can provide an excellent rinsing effect. In addition, although the impeller 204 has a large load in a predetermined rotation direction, since the injection of the washing water is also strong, the control device 212 can control the rotation direction to enhance the rinsing effect.

Thus, since the rinsing effect is high, the quantity and quality of dirt can reduce the frequency | count of a rinsing process, and can be set as the dishwasher which reduced the quantity of water used per washing operation, and the power consumption which passed the whole operation.

As the rotation control means of the electric motor 205, phase control and inverter control are also frequently executed. Of course, if the electric motor 205 is a DC brushless motor, the rotation speed can also be controlled in a wide range.

(Example 13)

27 is a general view of the dish washing dryer of the present embodiment.

In Figs. 27 and 28, reference numeral 301 denotes a first centrifugal blade, reference numeral 302 denotes a second centrifugal blade having a larger outer diameter than the first centrifugal blade 301, and reference numeral 303 denotes a suction port of fluid. It is a casing which has 304 and the discharge port 305. Reference numeral 306 denotes an electric motor for driving these centrifugal blades, and the casing 303 seals a fluid to the container main body 303a incorporating the centrifugal blades and the output shaft portion of the electric motor 306 inside the casing 303. It is formed of the container cover 303c which has the axial sealing member 303b. The first centrifugal vanes 301 and the second centrifugal vanes 302 are separate, but each have substantially cylindrical magnetic bodies 307 and 308 (magnet coupling), and the first centrifugal vanes 302 are electric motors 306. It is fixed with respect to the output shaft of. In addition, the second centrifugal blade 302 transmits torque from the first centrifugal blade 301 by the magnet couplings 307 and 308 and freely passes through the perturbation member 309 with respect to the output shaft of the electric motor 306. It is configured to rotate.

It is comprised as the washing | cleaning pump 310 using these as a main element. Reference numeral 311 denotes a dish container for storing the object to be cleaned, such as a dish or cooking utensil, and reference numeral 312 denotes a cleaning nozzle having a jet port for ejecting the washing water, and the discharge port 305 of the cleaning pump 310. Is connected to. Reference numeral 313 denotes a cleaning tank in which a dish container 311 or a cleaning nozzle 312 is incorporated. Reference numeral 314 denotes a water level detection means for detecting the cleaning level. Reference numeral 315 denotes a residual filter provided in the cleaning tank 313. In addition, a general drainage pump (not shown) is provided as a drainage means.

In addition, as shown in FIG. 29, when the rotation direction of a centrifugal vane turns clockwise, the inlet angle (alpha) 1 and the exit angle (beta) of the 1st centrifugal blade 301 are about 90 degrees or less. In addition, the exit angle (beta) 2 of the blade | wing 309 of the 2nd centrifugal blade | wing 302 is about 90 degrees or more. As a basic characteristic of such a wing, the second centrifugal blade 302 has an exit angle β2 of about 90 ° or more when the direction of rotation is clockwise, so that the circumferential speed at the time of rotation of the centrifugal blade is the same. The absolute velocity of the fluid is large due to the relationship between the velocity triangles at the outlet and the large suction force can be obtained even for the gas.

Therefore, compared with the 1st centrifugal blade 301, the 2nd centrifugal blade 302 has a suction force more than the 1st centrifugal blade 301 with a larger outer diameter than the circumferential speed of the same rotation speed. On the other hand, when the direction of rotation of the first centrifugal blade 301 is clockwise, the exit angle βl is 90 ° or less. Therefore, even if the circumferential speed at the time of rotation of the centrifugal blade is the same, the absolute velocity of the fluid is small and the speed is lower. The head can be converted to the pressure head with low loss, and has the feature that the liquid pressing force can be efficiently obtained. In addition, the torque setting of the magnetic bodies 307 and 308 (hereinafter referred to as the magnet coupling) is based on the torque of the electric motor 306 required to rotate the first centrifugal blade 301 at the time of pressurizing the washing water at the time of T1 and air pressurization. When the torque of the electric motor 306 required to rotate the second centrifugal blade 302 is set to T2, the release torque between the magnet couplings 307 and 308 (torque when the magnet coupling does not rotate together). Set T3 to be T1T3T2.

Next, the operation will be described. In a normal washing step, the first centrifugal blade 301 is rotated counterclockwise by the electric motor 306 to pressurize the washing water. The water guided from the suction port 304 to the casing 306 can be used as a general centrifugal pump because it is pressurized by the respective blades 301 and 302 and discharged from the discharge port 305.

By the way, when the water level detection means 314 detects the washing water level at a low water level, the quantity is small. At this time, in order for the cleaning pump 310 to circulate with a predetermined capacity, the water level drops rapidly during the process, and water including air is supplied to the cleaning pump 310. In a conventional dishwasher, when a large amount of air is mixed during operation, the pumpable state cannot be maintained. Therefore, the dish washing rate is lowered or, in some cases, the washing is not performed.

By the way, in the structure of a present Example, although the 1st centrifugal blade 301 makes the same rotation (for example, 3000 rotation) with the electric motor 306 during washing | cleaning, the load torque T which the 2nd centrifugal blade 302 receives is TT1, And rotation (900 revolutions) by inertia. Therefore, by simultaneously rotating the second centrifugal blade 302 together with the first centrifugal blade 301, the air to be retained in the casing 303 can be discharged.

In addition, since the outlet angle β2 of the second centrifugal blade is set to about 90 ° or more, the discharge speed of the air becomes higher. And if the injection energy of the washing | cleaning nozzle 312 makes the rotation speed of the electric motor 306 constant, a slight fall as much as the amount which mixed air compared with the normal washing | cleaning water level is seen, but the washing | cleaning pump 310 similarly conventionally The loss of the pressurizing ability as) will not lead to the problem that the cleaning nozzle 312 cannot be rotated.

Therefore, a predetermined cleaning power can be obtained as the dish washing machine. In addition, when the amount of air in the washing water further increases, the load torque T received by the second centrifugal blade 302 decreases, and the rotational speed thereof is closer to the rotational speed of the first centrifugal blade 301 to obtain its discharge capacity. Increase And when the casing 303 becomes almost all air (T2 <= TT3), the two blade | wings 301 and 302 rotate substantially the same, and exhibit predetermined blowing performance. In addition, the action of the two wings (301, 302) has the following characteristics.

First, in the washing step, the washing water is discharged mainly by the operation of the first centrifugal blade 301, but at this time, the washing water is discharged from the first centrifugal blade 301 by passing the washing water between the second centrifugal blades 302. There is a diffuser effect of rectifying the water to increase the efficiency.

In addition, at the time of discharge of air, air is discharged mainly by the operation of the 2nd centrifugal blade 302, but at this time, the 1st centrifugal blade 301 reduces the intake resistance to the 2nd centrifugal blade 302, and improves efficiency. Height exerts an effect as an inducer.

By using the magnet couplings 307 and 308 for driving transmission between the first centrifugal blade 301 and the second centrifugal blade 302 in this way, the ratio of the mixing ratio of the washing water and air supplied to the cleaning pump 310 According to the change (pump load), the rotational speed of the second centrifugal blade 302 along the first centrifugal blade 301 can be changed steplessly, and the air for blowing and drying the air for the discharge of the washing water can be changed. In addition to the two fluids called air blowing, the discharge of the mixed phase in which air and water are mixed can be used as the dish washing machine which realizes by one pump and a small electric motor.

In addition, when realizing the 1st centrifugal blade 301 and the 2nd centrifugal blade 302 with an integral blade, the electric motor 306 requires high torque which is expensive and large.

However, in the present invention, the load torque fluctuation is automatically adjusted by the magnetic bodies 307 and 308, and the outlet angle β2 of the second centrifugal blade 302 is set to about 90 ° or more, thereby reducing the load torque. The motor can be miniaturized.

Moreover, the height of the washing | cleaning mechanism part comprised with a washing | cleaning means and a washing | cleaning pump can be made small, and the dish washing volume can be enlarged without changing a product height. In addition, even when air is mixed during the cleaning, the pump capacity can be quickly restored, so that a dish washing machine capable of always obtaining a stable cleaning performance can be provided.

Moreover, since the detection precision of the water level detection means is a general thing, it can be set as the dishwasher which can be comprised at low cost.

Although the inlet angles of the first centrifugal blade 301 and the second centrifugal blade 302 are also considered to be 90 °, 90 ° or more or 90 ° or less, respectively, the effects of the present invention are sufficiently obtained in these cases. In addition, although the 1st centrifugal blade 301 and the 2nd centrifugal blade 302 were demonstrated as an open wing without a shroud, as shown in FIG. 4, even if a wing with a shroud is basically obtained, the effect of this invention is acquired. Needless to say.

(Example 14)

Since the basic configuration is the same dishwasher as in the thirteenth embodiment, the same description is omitted while sharing this. As shown in FIG. 31, it differs from Example 13 that the height of the 2nd centrifugal blade 317 is higher than the blade of the 1st centrifugal blade 301. As shown in FIG.

Since the basic operation | movement in the washing | cleaning process of a dishwasher is the same as Example 13, description is abbreviate | omitted. In the following, the operation is characterized by the features of the present invention.

In general, in a centrifugal pump, the fluid entering from the center portion of the centrifugal blade is discharged from the outer circumferential portion while receiving centrifugal force from the centrifugal blade, but a part thereof forms a secondary flow back to the centrifugal blade center portion that becomes negative pressure. This is one of the reasons for lowering the efficiency of the centrifugal pump.

By the way, in the structure of this embodiment, since the 2nd centrifugal blade 317 is formed to the upper part of the 1st centrifugal blade 301 which generate | occur | produces a secondary flow, the 2nd centrifugal blade 317 which rotates unlike a general diffuser is The suction force can also be generated in this portion. For this reason, the fluid to return to the center part of the 1st centrifugal blade 301 can return by the suction force of the 2nd centrifugal blade 317, and can suppress generation | occurrence | production of a secondary flow. Therefore, the pump can be improved in performance, size and cost by improving efficiency.

As described above, according to the present invention, it is possible to provide a dish washing machine in which a reduction in pump input, size reduction, and cost reduction are realized by improving the efficiency of the pump, and the dish washing volume is enlarged and energy is saved. Moreover, when the drying system which blows air from an injection hole can implement | achieve a high air volume, it can provide the dishwasher which improved the drying performance, such as shortening of drying time.

(Example 15)

Since the basic structure is the dishwasher similar to Example 14, while sharing this, detailed description is abbreviate | omitted. In particular, as shown in FIG. 32, the difference between the outer diameter of the first centrifugal blade 301 and the inner diameter of the second centrifugal blade 302 is equal to or greater than the maximum diameter of the dirt passing through the residual filter 315. It is set to.

When the dishwasher is operated, various kinds of residues such as toothpicks and rubber bands are introduced into the dishwasher in addition to the food attached to the dishware. Therefore, a remnant filter 315 is provided to protect the pump 310 so that these remnants do not enter the cleaning pump 310. In the design of the residual filter 315, the residual material having a certain diameter is allowed to pass through in consideration of securing the washing water in circulation and cleaning of the residual filter 315. Therefore, the cleaning pump 310 needs to consider the foreign matter having a diameter passing through the residue filter 315.

Therefore, according to the structure of this invention, since the clearance gap between the 1st centrifugal blade 301 and the 2nd centrifugal blade 302 is made larger than the maximum diameter of the residue which passes through the residue filter 315, for example, a broken piece of tableware, etc. Even if the solid matter of the inside enters into the washing | cleaning pump 310, it does not enter the clearance gap of the 1st centrifugal blade 301 and the 2nd centrifugal blade 302, and does not lock the washing pump 310. FIG. In addition, even if a foreign material that is somewhat larger than the maximum diameter of the residue passing through the residue filter 315 enters, the second centrifugal blade 302 is elastic by the magnet coupling 307 with respect to the first centrifugal blade 301. Due to the transmission structure, foreign matter caught in the gap between the first centrifugal blade 301 and the second centrifugal blade 302 is quickly removed.

Therefore, according to the present invention, it is possible to provide a dish washing machine capable of obtaining stable washing performance by securing high reliability against entry of foreign matters and the like.

(Example 16)

Since the basic configuration is the same dishwasher as in the thirteenth embodiment, this is shared and the overall configuration diagram is omitted. As shown in FIG. 33, the present embodiment is characterized in that the number of wings of the second centrifugal blade 302 is larger than the number of wings of the first centrifugal blade 301.

Next, the operation will be described. Since the basic thinking method is the same as that of the first embodiment, only the characteristic operation will be described.

As described in the first embodiment, the second centrifugal blade 302 rotates through the magnet couplings 307 and 308 outside the first centrifugal blade 301 fixed to the electric motor 306 during the cleaning. The rotation speed difference exists in both centrifugal vanes 301 and 302. This means that a part of the hydrodynamic energy of the washing water discharged from the first centrifugal vane 301 is used to rotate the second centrifugal vane 302, which means that the overall efficiency of the washing pump 310 is lowered.

Therefore, in the present embodiment, the number of wings of the second centrifugal blade 302 is configured to be larger than the number of wings of the first centrifugal blade 301 to increase the load torque received by the second centrifugal blade 302 at the time of cleaning, By lowering the rotation speed of the two centrifugal blades 302, the pressure conversion of the washing water can be performed effectively. Therefore, by suppressing the fall of pump efficiency, the pressurization characteristic required as a washing | cleaning pump can be acquired by a smaller motor.

In addition, by increasing the number of blades of the second centrifugal blade 302 when air is mixed in the washing water or during air blowing, recovery of cleaning performance due to early discharge of the mixed air, improvement of blowing performance during blowing, etc. Since a pump performance can be improved significantly comprehensively, the dishwasher which implements the improvement of washing | cleaning efficiency and drying performance can be provided.

In addition, in the said Example 13-Example 16, although the rotating washing | cleaning nozzle of the female shape is provided as a washing | cleaning means, it cannot be overemphasized that it is the same even if it is a fixed or substantially disk-shaped thing. In addition, the structure of a magnet coupling also has the cylindrical form as shown in FIG. 27, the disk form as shown in FIG. 34, the said two complex types (not shown), etc., but it is the same in either structure. Needless to say, the effect can be achieved. In the embodiment of the present invention, a magnetic body (magnet coupling) has been described as a torque transmission means between the first centrifugal vane and the second centrifugal vane. Instead, a fluid having an appropriate viscosity, such as a fluid coupling, is used. Needless to say, the effects of the present invention can be obtained even when using the torque transmission means using.

[Effects of the Invention]

As mentioned above, the washing | cleaning pump of the dish washing dryer of this invention has a hybrid impeller with a rear wing in an inner peripheral part, and a front wing in an outer peripheral part. The mixed phase impeller can pressurize and circulate air, water, and water containing air easily. Therefore, in all the embodiments of the present invention, the mixed phase impeller can be used not only as the impeller of the cleaning pump but also as the impeller of the drain pump or the impeller of the drying blower. When a mixed phase impeller is used as an impeller of a washing | cleaning pump, since a mixed phase impeller can pressurize water containing air, the level of washing water can be lowered in a washing | cleaning process. This results in saving water and the power required to warm the water. Further, in the drying step, the time for drying the dish can be shortened by rotating the mixed phase impeller at a higher speed than in the cleaning step and blowing air from the cleaning nozzle. The rinsing of the dishes is performed by draining the dirty washing water and supplying fresh water. However, some sewage remains undrained. Since the residual sewage soils the new water, in order to clean the rinsing water, the more the residual sewage, the more fresh water is required. When a mixed phase impeller is used as an impeller of a drain pump, since a mixed phase impeller can pressurize water containing air, sewage is drained until the residual amount becomes extremely small. Thus, fresh water for rinsing can be saved. In addition, when the mixed phase impeller is used as an impeller of a drying blower, since the inner blade acts as an inducer for drawing air into the impeller, a high air volume and high efficiency can be realized as compared with a normal sirocco fan. Further, when the outer diameter and the wing height are the same as those of a normal sirocco fan, the same performance can be ensured even if the rotational speed is lowered, so that the noise caused by the impeller can be reduced. In addition, although in Example 5 and Example 13, a shroud attachment wing is described as being able to be used similarly to an open wing without a shroud, the shroud attachment wing can be used similarly to an open wing without a shroud in all embodiments. Can be.

Claims (30)

A washing tank for holding the object to be cleaned, a washing means having a jet port for spraying the washing water, and a washing pump for pressurizing the washing water, wherein the washing pump includes a first centrifugal vane and a disc supporting the first centrifugal vane. An impeller disposed therein, a casing having an inlet and an outlet having an impeller built therein, and an electric motor for driving the impeller, wherein the wing shape of the first centrifugal vane has its inner circumference approximately an exit angle with respect to a predetermined rotational direction. A dishwashing dryer comprising a rear wing set at 90 ° or less, and a front wing set at an exit angle of about 90 ° or more on the outer circumferential portion, and the inner circumferential portion and the outer circumferential portion of the wing are connected in a curved shape. The method of claim 1, And a wing height of the outer circumferential front wing is set equal to or less than a wing height of the inner circumferential rear wing. The method according to claim 1 or 2, An outer circumferential front wing is divided into two parts in a substantially parallel direction with a disc, and some of the wings are configured with a second rear wing with an exit angle of about 90 ° or less and smoothly connected to the inner circumferential rear wing. The method of claim 3, wherein A dish washing dryer characterized by connecting the outer circumferential front end face and the rear end of the rear wing substantially in a plane without gap from the impeller outer circumference. The method according to any one of claims 1 to 4, The outer circumferential wing shape is a dish washing dryer, characterized in that the outlet angle is set to less than about 90 °. The method according to any one of claims 1 to 5, One or more third centrifugal vanes disposed between the vanes of the first centrifugal vanes may include a rear vane whose inner periphery has an inlet angle of about 90 ° or less and an outlet angle of about 90 ° or less with respect to a predetermined rotational direction. And a front wing having an outlet angle set at an exit angle of about 90 ° or more on the outer circumference thereof, wherein the wing inner diameter of the third wing is larger than the blade inner diameter of the first centrifugal blade. The method according to any one of claims 1 to 6, A dish washing dryer characterized by setting an inter-wing volume of the outer circumferential front wing to be equal to or greater than the inter-wing volume of the inner circumferential rear wing. The method according to any one of claims 1 to 7, A dish washing dryer characterized by setting an inter-wing volume of an outer circumferential front wing to be equal to or more than the sum of the impeller suction volume and an inter-wing rear volume of an inner circumferential rear wing. A washing tank for storing the object to be cleaned, washing means having an injection hole for spraying washing water, and a centrifugal pump as a washing pump for pressurizing the washing water, and the centrifugal pump includes a runner in which a first centrifugal vane is disposed; A casing having a suction port and a discharge port therein, and an electric motor for driving the runner, wherein the wing shape of the first centrifugal blade has its inner side set at an exit angle of about 90 ° or less with respect to a predetermined rotation direction. The shape portion and the front wing portion having the exit angle set at an exit angle of about 90 ° or more, and the inlet angle is about 90 ° or more with respect to a predetermined rotational direction and the exit angle is approximately between the first centrifugal blades, respectively. It is characterized by having one or more second centrifugal wings having a substantially curved front wing shape set to 90 ° or more and shorter than the wing height of the first centrifugal wing. Dish washer dryer as. The method of claim 9, A dish washing dryer characterized by connecting a rear wing portion and a front wing portion of the first centrifugal blade in a substantially curved smooth shape. The method according to claim 9 or 10, Among the plurality of second centrifugal vanes disposed between the first centrifugal vanes, the inlet angle of the second centrifugal vanes at a position preceding to the predetermined rotational direction and facing the first centrifugal vanes is the inlet angle of the other second centrifugal vanes. A dish washing dryer, characterized in that the larger setting. The method according to any one of claims 9 to 11, Among the plurality of second centrifugal vanes disposed between the first centrifugal vanes, the inner diameter of the second centrifugal vanes at a later position with respect to the predetermined rotational direction and facing the first centrifugal vanes is larger than that of the other second centrifugal vanes. A dish washing dryer, characterized in that set. The method according to any one of claims 9 to 12, The distance between the first centrifugal vane and the vanes of the second centrifugal vanes at opposite positions from the first centrifugal vanes relative to the predetermined rotational direction is advanced from the distance between the second vanes or from the second centrifugal vanes relative to the predetermined rotational direction. And greater than the distance between the vanes with the first centrifugal vanes at opposite positions. A washing tank for holding the washing water, a washing nozzle having an injection hole for injecting the washing water, and a washing pump for pressurizing the washing water by an impeller driven by an electric motor. A dish washing dryer comprising an inner blade and a plurality of outer blades provided on the outer side with respect to the rotation center. The method of claim 14, The shape of the inner blade is a rear shape inclined backward with respect to the predetermined rotation direction of the impeller, and the shape of the outer wing is forward with respect to the predetermined rotation direction of the impeller so that the fluid easily flows out to the outer circumference at the outermost part of the impeller. A dish washing dryer characterized by having a shape portion. The method according to claim 14 or 15, A dish washing dryer characterized by having a larger number of wings of an outer wing than the number of wings of an inner wing. The method according to any one of claims 14 to 16, The outer wing is composed of an outer wing and an outer wing, and in the height from the surface of the impeller, the outer wing is lower than the outer wing and the inner wing, and thus the distance to the inner surface of the casing of the cleaning pump in which the impeller is incorporated. The dishwashing dryer according to claim 1, wherein the outer wing is larger than the outer wing and the inner wing, and the outer wing is disposed in the gap between the outer wing on the extension of the gap between the inner wing. The method according to any one of claims 14 to 17, It includes a forward and reverse reversing means of the electric motor to select the rotation direction of the impeller of the cleaning pump so as to change the intensity of the injection pressure of the cleaning nozzle between each step of the cleaning step or to alternately change the injection pressure in each step. A dish washing dryer comprising a control device. The method according to any one of claims 14 to 18, The dish washing dryer provided with the control apparatus which drives the impeller of a washing | cleaning pump in the reverse rotation direction to a predetermined rotation direction, when the washing | cleaning water is below predetermined temperature in a washing | cleaning process. The method according to any one of claims 14 to 19, And a drainage pump for discharging the washing water out of the dishwashing dryer, wherein a control device for driving the impeller of the washing pump in the reverse rotational direction is provided in parallel with the operation of the drainage pump in the drainage process. The cleaning tank includes a cleaning tank for storing the object to be cleaned, a cleaning means having a jet port for injecting cleaning water, a filter for separating the dirt during cleaning, and a cleaning pump for pressurizing the cleaning water, and the cleaning pump is driven by an electric motor. A first centrifugal vane and a second centrifugal vane having a larger outer diameter than the first centrifugal vane, and having a casing having a suction port and a discharge port at the same time as those built-in centrifugal vanes; A dish washing dryer comprising a magnetic body that transmits torque to a position at which the vanes and the second centrifugal vanes respectively face each other. The method of claim 21, The dish shape of the second centrifugal blade has a straight or approximately curved front wing shape having an exit angle of about 90 ° or more. The method of claim 22, The vane shape of the first centrifugal vane has a straight or roughly curved rear vane whose inner part is set at an exit angle of about 90 ° or less with respect to a predetermined rotational direction. The method according to any one of claims 21 to 23, The blade height of a 2nd centrifugal blade was made higher than the blade height of a 1st centrifugal blade, The dish washing dryer characterized by the above-mentioned. The method according to any one of claims 21 to 24, A dish washing dryer, wherein a dimension difference between the outer diameter of the first centrifugal blade and the inner diameter of the second centrifugal blade is set to be equal to or larger than the maximum diameter of the dirt passing through the filter. The method according to any one of claims 21 to 25, A dish washing dryer, wherein the number of wings of the second centrifugal vane is greater than the number of wings of the first centrifugal vane. 27. The method of any of claims 21 to 26, T1 is the torque of the motor 6 required to rotate the first centrifugal vane 1 at the time of pressurizing the washing water, and T2 is the torque of the motor 6 required to rotate the second centrifugal vane 2 at the time of air pressurization. And a degassing torque T3 between the magnetic bodies and T1T3T2. And a cleaning device having a cleaning tank for holding the object to be cleaned, a cleaning means having a jet port for injecting cleaning water, a cleaning pump for pressurizing the cleaning water, and a control device for controlling rotation of the cleaning pump. A rear-finged blade and a mixed-phase impeller with a front wing on the outer circumference, wherein the control device makes the rotation of the cleaning pump during the drying process faster than during the cleaning process. A washing tank for holding the object to be cleaned, a washing means having a jet port for injecting washing water, a washing pump for pressurizing the washing water, and a drain pump for draining the washing water, wherein the drain pump includes a rear wing at an inner circumference thereof. And a dish washing dryer having a mixed impeller with front wings at its outer circumference. A washing tank for holding the object to be cleaned, a washing means having a nozzle for injecting the washing water, a washing pump for pressurizing the washing water, and a drying blower for supplying drying air, wherein the drying blower includes an inner peripheral portion. A dishwash dryer having a rear wing and a hybrid impeller with a front wing on the outer circumference.