JPH0925868A - Impeller and fluid driving device using same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize high safety, high efficiency and low cost in an impeller for a fluid driving device using fluid energy for driving. SOLUTION: Single side open type front blades 61B, 63B are provided on the single sides of impeller base parts 61A, 63A, and single side open type rear blades 61C, 63C and power transmission bodies 67, 68 are provided on the other single sides of the impeller base parts 61A, 63A. Communicating holes 61D, 63D are provided to communicate the front blade 61B, 63B side with the rear blade 61C, 63C side.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a circulation pump that uses as a power source a high-temperature heat medium that is forcibly circulated in each dwelling unit such as a central hot water supply system or a hot water supply and heating system of a dwelling such as an apartment house.

[0002]

2. Description of the Related Art As a conventional pump using a fluid as a drive source, there is, for example, a structure shown in FIG. 15 of Japanese Patent Laid-Open No. 3-279521.

FIG. 15 is a pump for taking river water from a river and pumping it by using the flow of the river water. A horizontal turbine equipped with an axial runner 1 and a horizontal turbine 2 and a single-stage impeller 3 are provided. An axial mixed flow type pump 4 is uniaxially connected via a speed increaser 5 and is housed in a casing 6.

In this structure, the river water upstream of the intake channel flows in from the suction pipe 7 due to its head to operate the water turbine 2, and a part of it is driven by the pump 4 driven by the water turbine 2 via the speed increaser 5. Is pressurized and is sent through the water pipe 8, and most of the river water that has operated the water turbine 2 is discharged to the downstream of the intake channel and flows out to the downstream of the river.

As another example of a conventional pump using a fluid as a driving source, FIG. 1 of Japanese Utility Model Laid-Open No. 58-195644 is used.
There is a structure as shown in FIG.

FIG. 16 is a pump for rotating a water wheel by the force of a fluid flowing through a pipe system to drive a constant amount discharge device such as a roller pump to suck and discharge a small amount of a chemical solution and inject it into the pipe system. An output shaft 11 of a water turbine composed of an impeller group 10 that obtains a rotational force proportional to the flow rate of a fluid flowing therein, is connected to a drive shaft 13 of a pump unit 12 by penetrating and protruding outside the piping system. 11 is supported by bearings 14 and 15 and is sealed by a shaft seal member 16.

In this structure, the impeller group 10 is rotated by the force of the fluid flowing in the piping system 9 in proportion to the flow rate of the fluid to operate the water turbine, and the pump portion 12 directly connected via the output shaft 11 is connected. It is driven to suck the chemical solution 18 from the chemical solution tank 17 through the tube 19 and inject it into the piping system.

FIG. 17 shows an example of a conventional hot water supply / room heating device for central housing. That is, the heat medium (high-temperature hot water) is circulated toward each dwelling unit, and the heat medium and the low-temperature water from the water supply pipe are heat-exchanged at each dwelling unit to heat and heat the hot water. The heat medium outward pipe 21 is arranged toward each floor and each dwelling unit of the dwelling, and the heat medium return pipe 22 connected at the end of the heat medium outward pipe 21 is arranged. 23, and the heat source side heat medium passage 2
3 is provided with a heat medium circulation pump 24.

The hot water supply / room heating device 25 of each dwelling unit is composed of the heat transfer pipe 2
1 is connected to the heat medium hot water supply forward pipe 26, and is connected to the heat medium return pipe 22 via the first control valve 27 and the heat medium hot water return pipe 28 to form a hot water supply primary side system passage 29, and water is supplied at the inlet side. A hot water supply heat exchanger 33 is provided which communicates with the pipe 30 and has a hot water supply secondary side system passage 32 having a hot water supply tap 31 at the end on the outlet side in a heat exchange relationship. A heating primary side system passage 37 formed by the heating medium heating outward pipe 34, the second control valve 35, and the heating medium heating return pipe 36 is provided in parallel with the heating medium hot water returning pipe 26 and the heating medium hot water returning pipe 28, A heating secondary side system passage 42 which communicates with the heating outward pipe 39 from the systurn 38 on the inlet side and a heating radiator 40 and a heating return pipe 41 are arranged on the outlet side in this order to form a circulation system passage A heating heat exchanger 43 in an exchange relationship is provided. In addition, the bath-fired forward pipe 44,
Heat exchanger 4 for bath reheating built in Sistern 38
5. A bath reheating system passage 47 configured by arranging the bath reheating recuperation pipe 46 in this order is connected to the bathtub 48. In addition, a heating pump 49 is provided in the system path of the heating outward pipe 39, and a bath pump 50 is provided in the bath reheating system path 47.

The hot water supply / room heating device 25 operates the heating pump 49 driven by an electric motor to send the high temperature hot water obtained by the heating heat exchanger 43 to the heating radiator 40 for heating, and the electric motor. The high-temperature hot water obtained by the bath-exchanging heat exchanger 45 is driven to drive the bath pump 50, which is then driven to the bath, to supplement the bath.

Further, as a pump using an electric motor as a drive source, there is one having a structure as shown in FIG. 18 of Japanese Utility Model Laid-Open No. 57-40686.

FIG. 18 shows a drive shaft 51 of an electric motor 50m.
The drive-side magnet 53, which is a permanent magnet fixed to the rotating body 52 fixed to, is provided to face the driven-side magnet 55, which is a permanent magnet fixed to the pump impeller 54, via a partition wall 56. The pump impeller 54 is housed in the pump casing 57 and the pump casing 5
It is rotatably attached to a fixed shaft 58 provided on the No. 7.

In this structure, when the drive shaft 51 is rotated by the electric motor 50m, the drive side magnet 53 is rotated together with the rotating body 52 integrated with the drive shaft 51, and the driven side magnet 55 connected by magnetic force is rotated together with the pump impeller 54. Then, the fluid sucked from the suction port 59 is sent out from the discharge port 60 by centrifugal force.

On the other hand, Japanese Patent Application Laid-Open No. 55-57697 discloses that the pump impeller is directly rotated by the drive shaft.
There is a structure as shown in FIG. 19 of the publication.

FIG. 19 shows the main board 10 of the pump impeller 101.
A plurality of blades 103 protruding axially on both sides of
104 is provided, side plates 105 and 106 are attached to the tips of the blades 103 and 104, respectively, and suction passages 107 and 108 and a suction port 109 are provided on both sides of the pump impeller 101.
This is a double-suction type and closed-type impeller provided with 110, and a drive shaft 112 is attached to a boss portion 111 to be rotationally driven from the outside.

In this structure, the pump impeller 101 rotated by the drive shaft 112 has the suction ports 109 on both sides,
The fluid sucked from 110 is pumped by centrifugal force 1
01 to the outer peripheral side, and then to the outer peripheral side annular passage 113.

[0017]

However, the hot water supply and heating device 25 provided in each dwelling unit for the central of the conventional dwelling building is provided.
With this configuration, the heating pump 49 and the bath pump 50 are operated when heating and reheating the bath. All of these are pumps driven by an electric motor. Therefore, these two pumps have the problems that the initial cost is high, the size is large, the weight is heavy, and the running cost is high because they consume electricity.

Although there is a method in which the driving power of the pump is performed by the fluid force of the fluid, in the conventional configuration shown in FIG. 15, the rotational speed of the water turbine is low and the rotational speed required for driving the pump by the water turbine itself can be obtained. It is not necessary to install a speed increaser on the way,
The initial cost is high and it cannot be used for general households, and the fluid driven by the water turbine and the fluid conveyed by the pump are not separated and are exactly the same. Had safety and hygiene issues.

Further, in the conventional construction shown in FIG. 16, the drive side fluid and the fluid conveyed by the pump are partitioned by the shaft seal member in the pump portion, but are used for the central hot water supply of the dwelling. In case of emergency, it is uncertain how to prevent the mixture of fluids on the drive side and the pump side, which poses a reliability problem.Because of the shaft seal member, the rotation resistance of the output shaft of the water turbine is large, so The flow rate on the pump side was too small to be used for heating, etc., and there was a problem with flow rate characteristics.

Therefore, we proposed a fluid drive pump disclosed in Japanese Patent Laid-Open No. 6-185489 and made improvements.
As a result, it has been found that it is important to reduce the rotational resistance as much as possible in order to effectively utilize the limited driving force of the driving fluid, and it is not negligible that the electric motor type pump only increases the motor input. .

That is, in the conventional structure shown in FIG. 18, since the driven magnet 55 occupies the partition wall 56 side of the pump impeller 54, the shaft in the direction of the suction port 59 generated by the fluid force during the operation of the pump impeller 54. The thrust force in the axial direction cannot be reduced, and the frictional resistance in the bearing portion caused by the axial thrust force increases.

As a method of reducing the axial thrust force, there is a double-suction type impeller shown in FIG. 19. However, since it has a drive shaft, the rotational resistance of the shaft seal member and the rotation resistance of the shaft seal member are the same as in the conventional example shown in FIG. There is a problem in preventing both fluids on the drive side and the pump side from entering, and there is a problem in downsizing because the size of the suction passage space is increased on both sides due to the double suction structure.

The present invention is intended to solve the above problems, and it is a first object of the present invention to provide a highly efficient impeller which can be used for central hot water supply in a residential building, is small and compact, has a low initial cost. . A second object of the present invention is to provide a fluid-driven circulation pump that can be used for central hot water supply in a residential building, is compact, has high safety, and reduces driving fluid power. Furthermore, the third object is to provide an impeller with improved power transmission capability. The fourth purpose is to improve the efficiency of the impeller, and the fifth purpose is to further reduce the size of the impeller. The sixth purpose is to improve.

[0024]

In order to achieve the first object of the present invention, a single-sided open type front blade provided on one side of a blade base and a single-sided open type back blade on the other side of the blade base. The blade has a blade and a power transmission body, and is provided with a communication hole that connects the front blade side and the back blade side.

Further, in order to achieve the second object, a drive impeller having a primary fluid as a drive source of rotational force, a secondary impeller for circulating a secondary fluid, and the primary fluid A partition wall that airtightly separates the secondary fluid, a drive-side power transmission body provided in the drive impeller, and a driven-side power transmission body provided in the secondary side impeller are opposed to each other through the partition wall. Power transmission means, at least one of the drive impeller and the secondary side impeller, a front blade of one side open type provided on one side of the blade base, and a back blade of one side open type on the other side of the blade base. And the power transmission body, and is mounted with an impeller having a communication hole that communicates the front blade side and the back blade side.

In order to achieve the third object, the power transmission means is provided on the outer peripheral side of the back blade, and the communication holes are provided on the inner peripheral side and the outer peripheral side of the back blade.

Further, in order to achieve the fourth object, the power transmission body is provided on the outer peripheral side of the back blade, and the recessed groove portion extending to the outer peripheral side and the inner peripheral side of the power transmission body is provided.

In order to achieve the fifth object, the power transmission means is provided on the inner peripheral side of the back blade, and the communication hole is provided on the outer peripheral side of the power transmission body.

Further, in order to achieve the sixth object, the communication hole is such that the middle of the flow path of the front blade and the inner peripheral side of the back blade communicate with each other.

[0030]

According to the present invention, according to the above-mentioned structure, the first means has the one-sided open type blades on both sides of the blade base portion, so that the thrust force in the axial direction is canceled and the rotational movement with less thrust resistance is performed. Since the axial mouth of the impeller is arranged on only one side, the size is reduced.

In the second means, the primary side fluid is caused to flow to the drive impeller to rotate the drive impeller, and the powers are opposed to each other via the partition wall that airtightly separates the primary side fluid and the secondary side fluid. The secondary side impeller, which is connected to the drive impeller in a non-contact manner, rotates by the power transmission means by the transmission body, and the pump operation for conveying the secondary side fluid is performed. At this time, the driving impeller or the secondary-side impeller has single-sided open-type blades on both sides of the blade base, so that the thrust force in the axial direction is canceled out and the rotary motion with less thrust resistance is performed, and the drive of the primary-side fluid is performed. Fluid power is reduced.

In the third means, the radius of the power point for applying the rotational force is increased (the moment force is increased) by providing the power transmission body on the outer peripheral side of the back blade, and the power transmission capability is increased by the larger torque transmission. Driving is performed with a higher level.

Further, in the fourth means, the outer peripheral portion of the back blade is communicated with the outer peripheral side of the power transmission body through the concave groove portion,
In the driving impeller, not only the front blade but also the concave groove part receives the fluid force of the driving fluid to increase the driving force, and in the secondary side impeller, part of the fluid that has passed through the back blade is in the concave groove part. The operation is performed and the pumping characteristics are improved by receiving the rotational force.

In the fifth means, the power transmission body is provided on the inner peripheral side of the back blade to downsize the secondary side impeller or the drive impeller to reduce the inertial force.

In the secondary impeller, the sixth impeller has a driving impeller in which the fluid whose pressure is being boosted is introduced into the back vane by the front vane to improve the pump characteristic of the back vane. In the case of (1), the fluid that has flowed out from the back blade is joined in the middle of the front blade to perform an operation in which the rotational force is further increased.

[0036]

Embodiments of the present invention will be described below with reference to FIGS. First, the first and second embodiments of the present invention shown in FIGS. 1 and 5 will be described. In the figure, 61 is a drive impeller provided in a drive fluid passage 62 through which the primary fluid flows, and uses the primary fluid as a drive source of rotational force, and 63 is provided in a driven fluid passage 64 through which the secondary fluid flows. It is a secondary-side impeller that circulates the secondary-side fluid. Reference numeral 65 is a partition that hermetically separates the drive fluid passage 62 through which the primary fluid flows and the driven fluid passage 64 through which the secondary fluid flows. 6
Reference numeral 6 denotes a power transmission means, and a drive-side power transmission body 67 fixedly provided on the drive impeller 61 and a driven-side power transmission body 68 provided on the secondary side impeller 63 face each other via a partition wall 65. Are arranged. Drive impeller 61 and secondary-side impeller 63
Are arranged so as to face each other through the partition wall 65, and are connected by a power transmission means 66 so that power can be transmitted.
Reference numeral 69 denotes a drive-side support shaft that rotatably supports the drive impeller 61, and 70 denotes a secondary-side support shaft that rotatably supports the secondary-side impeller 63. Both support shafts are supported by the partition wall 65. There is.

Reference numeral 71 denotes a drive inlet into which the primary side fluid flows, 7
Reference numeral 2 is a drive outlet through which the primary fluid flows out, and 73 is a secondary inlet through which the secondary fluid flows. 74 is the secondary side impeller 63
Is a secondary side outlet that is opened to the pump chamber 75 that stores the secondary side fluid and is sucked from the secondary side inlet 73 by the operation of the secondary side impeller 63 to be pressurized and flow out.

Drive impeller 61 and secondary-side impeller 63
Are the blade bases 61A, 63A on one side of the blade bases 61A, 63A on the drive outlet 72 side or the secondary side inlet 73 side, respectively.
A plurality of front blades 61B protruding from 63A and extending in the radial direction,
63B is provided, and a plurality of back blades 61C and 63C that project from the blade bases 61A and 63A and extend in the radial direction are provided on the side of the partition wall 65 that is the other surface of the blade bases 61A and 63A. Front blades 61B, 63B and back blade 6
The front end portions in the height direction rising from the blade base portions 61A and 63A of 1C and 63C are so-called open type blades having no side wall.

61D and 63D are blade base portions 61, respectively.
Front blades 61B, 63B side and back blade 6 through A, 63A
The communication holes 61D and 63D are communication holes that communicate with the 1C and 63C sides. The communication holes 61D and 63D are inclined holes having inclined surfaces 61F and 63F in the circumferential direction as shown in FIG. 4 (A-A cross section in FIG. 2). Reference numerals 61E and 63E denote a drive side bearing and a secondary side bearing provided on the blade base portions 61A and 63A. Reference numeral 76 is a thrust body that is provided at both ends of the drive impeller 61 and the secondary side impeller 63 and that receives thrust force in the axial direction.

The operation of the impeller in the above structure will be described. First, when used as a secondary side impeller that performs a pumping action, when the impeller 63 rotates in the direction of arrow P shown in FIG. 2, the fluid flows in the axial direction around the secondary side bearing 63E on the front blade 63B side. At the same time, a part of them is pressurized by centrifugal force through the passage between the front blades 63B and flows out from the outer peripheral portion, and the rest passes through the communication hole 63D and enters the side of the back blade 63C to pass through the passage between the back blades 63C. It is pressurized by centrifugal force and flows out from the outer peripheral portion. This communication hole 63D has an inclined surface 61.
Since it is an oblique hole due to F, not only the flow resistance of the fluid is reduced, but also the fluid passing through the communication hole 63D is applied with a fluid force toward the back blade 63C by the rotation of the impeller 63.

Further, a drive impeller 6 for generating a rotational drive force
When used as 1, the front blade 61B and the back blade 61C are rotationally driven by the fluid pressure of the fluid ejected in the circumferential direction R of the impeller 61 so as to rotate in the direction of the arrow Q shown in FIG. Fluid flows axially from around the drive-side bearing 61E through the passage between the front blades 61B on the front blade 61B side, and the remaining fluid passes through the passage between the back blades 61C on the back blade 61C side toward the center direction. Toward the front, the fluid passes through the communication hole 61D, merges with the fluid on the front blade 61B side, and flows out in the axial direction. Here, since the communication hole 61D is an inclined hole due to the inclined surface 61F, the flow resistance of the fluid is reduced and the communication hole 6D is formed.
The fluid flowing through 1D further applies a rotational force to the impeller 61 in the direction of the arrow Q to increase the rotational driving force.

As described above, the blade base 61A, which is used for both the drive impeller 61 and the secondary side impeller 63,
Front blades 61B, 63B and back blade 6 on both sides of 63A
Since 1C and 63C are provided and the tip of the blade is an open type blade without a side plate, the axial thrust force of the fluid is reduced, and the mechanical frictional resistance at the ends of the bearings 61E and 63E can be reduced. Since it is an open type impeller, there is no disc friction loss, which is fluid friction resistance, and rotation resistance can be reduced, improving efficiency.

Further, the communication holes 61D and 63D are the blade base 6
By providing inclined surfaces 61F and 63F in the circumferential direction with respect to 1A and 63A, the communication holes 61D and 63D newly generate the action of blades, and the rotational driving force is increased in the driving impeller,
Further improvement of the characteristics of the impeller can be realized, such as improvement of pump transfer characteristics in the secondary side impeller that performs the pumping action.

Although FIG. 2 and FIG. 3 show the case where the front blade and the back blade have the same shape, the back blade 61C ′ has the blade base portions 61A and 63A as shown in FIG. 5 as another embodiment. , 63C 'can be added to expand the degree of freedom in design for arbitrarily changing the shapes of the front and back blades.
The blade characteristics of 3B and the rear blades 61C and 63C can be optimized, and the efficiency can be further improved.

Further, even though the blade bases 61A and 63A are provided with blades on both sides, the communication hole allows one side of the inner peripheral side of the impeller (the drive outlet 7 in the drive impeller 61).
2. Since the secondary side impeller 63 is the secondary side inlet 73), the cost and size can be reduced by simplifying the configuration of the impeller.

As described above, according to the first embodiment of the present invention, the impeller is suppressed by reducing the mechanical frictional resistance due to the axial thrust force and suppressing the disc friction loss which is the fluid frictional resistance. There is an effect that high efficiency can be realized.

Further, there is an effect that cost reduction and size reduction can be realized by the double-sided blade and the single-sided inlet / outlet structure. Further, there is an effect that the degree of freedom in designing the front and back blades can be improved and the efficiency can be further improved by optimizing the front and back blades.

Next, the operation of the fluid drive system having the structure shown in FIG. 1 will be described. The drive-side impeller 61 rotates around the drive-side support shaft 69 together with the drive-side power transmission 67 by the primary-side fluid ejected from the drive inlet 71, and the secondary-side impeller having the driven-side power transmission 68. Since 63 is connected in a non-contact manner by the power transmission means 66, it rotates about the secondary side support shaft 70. At this time, the drive inlet 71
The primary fluid ejected from the front blade 61B and the back blade 6
1C flows in from the outer peripheral side to generate the rotational force of the drive impeller 61, flows out from the inner peripheral side toward the drive outlet 72. The fluid that has entered the back blade 61C passes through the communication hole 61D on the inner peripheral side and merges with the front blade 61B side.

On the other hand, on the driven fluid passage 64 side, the fluid in the driven fluid passage 64 flows into the pump chamber 75 from the secondary inlet 73 due to the rotation of the secondary side impeller 63, and part of the fluid is driven by the front blade 63B. The remaining portion passes through the communication hole 63D, is pressurized by the back blade 63C by centrifugal action, and flows out from the secondary side outlet 74.

Thus, even if this impeller is used for both the drive impeller 61 and the secondary side impeller 63, the impeller base 6
The front blades 61B and 63B and the rear blades 61C and 63C are provided on both sides of 1A and 63A, and since the blades are open blades without side plates, the thrust force in the axial direction due to the fluid is small and the thrust at the ends of the bearings 61E and 63E. Mechanical frictional resistance with the body 76 can be reduced, and when there is a side plate, the side plate rotates and so-called disc friction loss, which is frictional resistance with the fluid, occurs, whereas in the present invention, there is no side plate open. Since it is a mold, the frictional loss of the disc does not occur and the rotation resistance can be reduced.
Due to such reduction of mechanical friction resistance and fluid friction resistance, high efficiency with less loss can be realized, and a fluid drive device that has a small drive fluid power and performs a secondary action such as a pump action can be obtained. The load on the driving fluid can be reduced and the driving fluid power can be reduced.

Further, although the impeller has blades provided on both sides of the blade base, the inner peripheral side of the impeller has one side (the secondary side impeller 63 has a secondary inlet 73, and the driving impeller 61 has a drive outlet 72). Since the power transmission bodies 67 and 68 are provided on the other surface and face each other, the structure and the size of the fluid drive device can be simplified.

As described above, according to the second embodiment of the present invention, in contrast to the conventional electric motor type pump composed of the complicated electric motor and one impeller, the electric motorless and two blades are provided. Since the size of the pump can be reduced and the weight of the pump can be reduced, the initial cost is low, and the electric bill generated in the case of the electric motor type pump is not required, the running cost can be reduced.
This is similar to the case of the fluid drive pump shown in Japanese Patent No. 5489.

Further, by reducing the thrust force in the axial direction, it is possible to reduce the mechanical friction resistance in the bearing portion and suppress the fluid friction resistance such as the disc friction loss, and it is possible to realize a highly efficient fluid drive device. is there.

Further, the load of the driving fluid power on the primary side can be reduced, and a larger work can be performed on the secondary side, which is the user side, by using the limited driving fluid power on the primary side. (Heating, hot water supply, reheating the bath, etc.) can be expanded, or the range of use (increasing the heating capacity output, etc.) can be expanded, and the practicality is improved.

Further, by arranging the impellers having a simplified structure so as to face each other, it is possible to reduce the size of the fluid drive device.

Although the drive impeller 61 and the secondary-side impeller 63 have the same shape in this embodiment, the drive impeller 61 and the secondary-side impeller 63 have different blade shapes. It is possible to change, and both the driving impeller 61 and the secondary side impeller 63 have shown the case of the impeller having the front blade and the back blade on both sides of the blade base, but either one of the blade base has It goes without saying that an impeller having front and back blades on both sides and an impeller having only front blades can be provided on the other side.

Next, a third embodiment of the present invention shown in FIGS. 6 to 8 will be described. The same functions and members as those in the embodiment shown in FIGS. 1 to 5 are designated by the same reference numerals and detailed description thereof will be omitted.

67A is a blade base portion 61A of the driving impeller 61.
Is a drive-side power transmission body provided on the partition wall 65 side of the open type back blade 61CA, and 68A of the drive type power transmission body on the partition wall 65 side of the blade base portion 63A of the pump impeller 63 and the open type back blade 63CA. It is a power transmission body provided on the outer peripheral side. In the blade base 61A of the drive impeller 61, a communication hole 6 on the inner peripheral side that connects the inner peripheral side of the back blade 61CA and the inner peripheral side of the front blade 61B.
1DA is provided with a communication hole 61DB on the outer peripheral side that connects the outer peripheral side of the back blade 61CA and the outer peripheral side of the front blade 61B. Further, in the blade base 63A of the pump impeller, a communication hole 63DA on the inner peripheral side that communicates the inner peripheral side of the open type rear blade 63CA and the inner peripheral side of the front blade 63B, and the outer peripheral side of the rear blade 63CA and the front blade. Communication hole 6 on the outer peripheral side that communicates with the outer peripheral side of 63B
3DB is provided. Communication holes 61DB, 6 on the outer peripheral side
3DB is back blade 61CA, front blade 61 from 63CA side
The blade bases 61A and 63A are provided obliquely so that the diameter of the opening position increases toward B and 63B.

The operation of the impeller in the above structure will be described with reference to the fluid drive system. In the drive impeller 61, the primary fluid ejected from the drive inlet 71 flows into the front blade 61B.
And a rotating force is generated, and a part of the front blade 61B
A rotary force is applied to the drive outlet 72 through the passage between them, and the rest collides with the front blades 61B and then passes through the communication hole 61DB on the outer peripheral side and is jetted to the back blades 61CA, where the rotary force is also applied to the inside. Front blade 61 through communication hole 61DA on the circumferential side
It merges with the fluid on the B side and flows out to the drive outlet 72. The rotation of the drive impeller 61 is controlled by the power transmission body 67A fixed to the outer peripheral portion of the blade base 61A so as to face the secondary side impeller 6.
The secondary side impeller 63 is transmitted to the power transmission body 68A on the third side.
Rotates in synchronization with the drive impeller 61.

On the other hand, on the driven fluid passage side 64, a part of the fluid sucked from the secondary side inlet 73 due to the rotation of the secondary side impeller 63 is pressurized through the passage between the front blades 63B and the secondary side. To the outlet 74, the rest passes through the communication hole 63DA on the inner peripheral side, enters the rear blade 63CA side, and is pressurized to the rear blade 6.
After passing through the communication hole 63DB on the outer peripheral side of 3CA, they are jetted to the front blade 63B side and merge.

As described above, since the power transmission means 66 is constituted by the power transmission bodies 67A, 68A provided on the outer peripheral sides of the back blades 61CA, 63CA, the radius of the power point for transmitting the power can be increased and the torque for transmitting the rotational force can be transmitted. It is possible to realize an impeller with high power transmission capability.

Further, the communication holes 61DA and 63D on the inner peripheral side are provided.
In addition to A, since the communication holes 61DB and 63DB on the outer peripheral side are provided, the drive impeller 61 concentrates on the outer peripheral portion of the front blade 61B to eject the fluid to enhance the driving force, and also the communication holes on the outer peripheral side. The fluid that has passed through 61DB is jetted again to the rear blades 61CA, and the operation with a higher driving force can be performed. Further, in the secondary side impeller 63, the fluid passing between the back blades 63CA is made to flow into the outer peripheral portion where the passage cross-sectional area between the front blades 63B is widened through the communication hole 63DB, and the outer peripheral portion between the front blades 63B is formed. Since the flow rate is increased, it is possible to realize an impeller with higher efficiency by reducing eddy loss due to separation of fluid from the blades on the outer peripheral portion of the front blade 63B or local backflow between the blades.

Further, the communication holes 61DB, 63DB on the outer peripheral side
By obliquely opening the blade bases 61A and 63A, it is possible to smoothly divide or join the fluid flows to realize a reduction in loss while preventing an increase in flow resistance.

Although the communication hole on the outer peripheral side is provided so that the diameter of the opening position increases toward the front blade,
It goes without saying that a smoother flow of the fluid can be formed by further opening not only in the radial direction but also in the rotation direction, that is, the circumferential direction (not shown), and a lower loss can be realized.

As described above, according to the third embodiment of the present invention, the same effect as that of the first embodiment of FIG. 1 can be obtained, and an impeller having a large transmission torque and a high power transmission capability can be realized. There is an effect. Further, the driving impeller can be operated with a higher driving force, and the secondary side impeller can realize a highly efficient impeller with reduced loss.

Next, a fourth embodiment of the present invention shown in FIGS. 9 to 12 will be described. The same functions and members as those of the embodiment shown in FIGS. 1 to 8 are designated by the same reference numerals and detailed description thereof will be omitted.

67B is a blade base portion 61A of the driving impeller 61.
Is a drive-side power transmission body provided on the partition wall 65 side and on the outer peripheral side of the back blade 61CA. 67C is a plurality of concave groove portions provided on the partition wall 65 side of the power transmission body 67B. The concave groove portions 67C are formed on the outer peripheral side and the inner peripheral side of the power transmission body 67B, and are arranged on the back blade 61CA side and the power transmission body. 67B
The fluid is connected to the outer peripheral side by a concave groove 67C. 68B is a blade base portion 63A of the secondary side impeller 63.
Is a driven-side power transmission body provided on the partition wall 65 side and on the outer peripheral side of the back blade 63CA. Reference numeral 68C denotes a plurality of concave groove portions provided on the partition wall 65 side of the power transmission body 68B. The concave groove portions 68C are formed on the outer peripheral side and the inner peripheral side of the power transmission body 68B, and the rear blade 63CA side and the power transmission body. 68B
The fluid is connected to the outer peripheral side by a concave groove portion 68C.

The operation of the impeller having the above structure will be described with reference to the fluid drive system. A part of the driving fluid flowing from the driving inlet 71 flows into the back blade 61CA through the front blade 61B and the communication hole 61DB on the outer peripheral side and gives a rotational force to the driving impeller 61 to be driven, as in the second embodiment. Outflow to the outlet 72, the rest is ejected to the outer peripheral portion of the drive-side power transmission body 67B, collides with the concave groove portion 67C, flows into the drive impeller 61, and further inflows to the rear blade 61CA side. On the side of the secondary side impeller 63, a part of the fluid sucked from the secondary side inlet 73 passes through the front blade 63B as in the second embodiment and from the communication hole 63DA on the inner peripheral side to the back blade. 63CA is discharged from the secondary side outlet 74 through the communication hole 63DB on the outer peripheral side, and the rest passes through the concave groove portion 68C on the outer peripheral side of the back blade 63CA toward the secondary side outlet 74.

As described above, in the drive impeller 61, the concave groove portion 67C effectively receives the fluid force and the back blade 61C.
It is possible to perform efficient operation by increasing the rotational force by causing the fluid to flow out to the CA side, and in the secondary side impeller 63, the fluid pressurized by the rear blade 63CA is reduced by the concave groove portion 68C and flows out while reducing the flow resistance to raise the pump head. Operation with good pump characteristics is possible.

FIG. 12 shows another embodiment, in which the driving and driven power transmission bodies 67B and 68B are magnets, and a plurality of 67D and 68D are formed on the driving and driven power transmission bodies 67B and 68B. The concave groove portions 67D and 6 are provided between the magnetic poles of the N pole and the S pole that are formed.
8D is provided between magnetic poles of at least N pole and S pole.

In the above structure, the magnetic pole surfaces are relatively projected by the concave groove portions 67D and 68D provided between the N and S poles. Therefore, the magnetic flux emitted from the magnetic poles is less likely to be interfered with by the magnetic flux emitted from the adjacent magnetic poles, and is concentrated on the opposing magnetic poles via the partition wall 65 as a power transmission body.

Therefore, the connecting force of the power transmitting means 66 is increased, and it is possible to connect the impellers having improved power transmitting ability, and the power transmitting bodies 67B and 68B can be downsized.

As described above, there is an effect that an impeller with improved power transmission capability can be realized. Further, there is an effect that a compact impeller in which the power transmission body is downsized can be realized.

As described above, according to the fourth embodiment of the present invention, the same effects as those of the first embodiment of FIG. 1 and the third embodiment of FIG. The operation can be performed with a higher force, and in the secondary-side impeller, there is an effect that flow resistance in the impeller is further reduced to increase the pump head, and there is an effect that efficiency is further improved and performance is improved.

In the present embodiment, the case where the concave groove portion has a quadrangular cross section is shown. However, the concave groove portion is formed into a saw-tooth shape (not shown) having a substantially triangular shape with respect to the rotation direction of the impeller, that is, the circumferential direction. It goes without saying that it is okay.

Next explained is the fifth embodiment of the invention shown in FIG. The same functions and members as those in the embodiment shown in FIGS. 1 to 5 are designated by the same reference numerals and detailed description thereof will be omitted.

The drive-side power transmission body 67 and the driven-side power transmission body 68 are provided on the inner peripheral side of the back blades 61CB and 63CB, and the communication holes 61D and 63D are provided in the power transmission bodies 67 and 68.
Is provided on the outer peripheral side. Also, the back blades 61CB, 6
Communication holes 61D and 63D are provided at the inner peripheral end of 3CB,
The power transmission bodies 67 and 68 and the back blades 61CB and 63CB are separated by the annular flow paths 77 and 78.

The operation of the impeller having the above structure will be described with reference to the fluid drive system. In the drive impeller 61, a part of the primary-side fluid that has flown out from the drive inlet 71 flows into the front blade 61B.
Collide into and generate the rotational force of the drive impeller 61, and the remaining fluid efficiently collides and flows into the rear blade 61CB because the outer peripheral side of the rear blade 61CB is open to generate a stronger rotational force. The drive outlet 7 passes through the communication hole 61D.
Head to 2. Further, in the secondary side impeller 63, a part of the fluid sucked from the secondary side inlet 73 due to the rotation of the secondary side impeller 63 is part of the front blade 6
The fluid is pressurized by 3B toward the secondary side outlet 74, the remaining fluid passes through the communication hole 63D, enters the back blade 63CB, is pressurized, and is smoothly discharged from the outer peripheral side of the back blade 63CB. The flow path resistance in the impeller 63 is greatly reduced. Further, since the power transmission bodies 67 and 68, which become heavy in weight, are arranged on the inner peripheral side, the impeller having a small inertia during rotation of the impeller and quick start-up / startup and excellent control response such as speed change can be provided. it can.

Further, the annular flow path 7 having no back blade in the communication holes 61D, 63D on the inner peripheral side of the back blade 61CB, 63CB.
Since 7, 78 are provided, it is possible to prevent the generation of power loss just by stirring the fluid in the circumferential direction, and realize highly efficient operation with less loss.

As described above, according to the fifth embodiment of the present invention, the same effect as that of the first embodiment of FIG. 1 can be obtained, and an impeller having higher performance with improved characteristics of the back blade can be obtained. There is an effect that it can be realized.

Further, there is an effect that an impeller excellent in startability or control response of speed change can be obtained.

Next explained is the sixth embodiment of the invention shown in FIG. The same functions and members as those in the embodiment shown in FIGS. 1 to 5 are designated by the same reference numerals and detailed description thereof will be omitted.

The driving-side power transmission body 67 and the driven-side power transmission body 68 are provided on the inner peripheral side of the back blades 61CC and 63CC, and the communication holes 61DC and 63DC are the power transmission bodies 67 and 63DC, respectively.
It is provided on the outer peripheral side of 68. Communication hole 61DC, 63
DC has one end opened in the middle of the flow path of the front blades 61B and 63B that has entered the outer peripheral side from the inner peripheral side tips of the front blades 61B and 63B, and the other end opened to the inner peripheral side tips of the back blades 61CC and 63CC. The middle of the flow passages of the front blades 61B and 63B and the inner peripheral side of the back blades 61CC and 63CC are communicated with each other. Further, the power transmission body 67 is provided at the communication holes 61DC and 63DC at the inner peripheral ends of the back blades 61CC and 63CC.
It has annular flow paths 77 and 78 separated from 68.

The operation of the impeller having the above structure will be described with reference to the fluid drive system. In the drive impeller 61, a part of the primary-side fluid that has flown out from the drive inlet 71 flows into the front blade 61B.
Collide into and generate a rotational force of the drive impeller 61, and the remaining fluid efficiently collides into the rear blade 61CB to generate a stronger rotational force because the outer peripheral side of the rear blade 61CB is open. Further, with residual pressure, communication hole 61D
After passing through C, they are jetted and merged to the front blade 61B side to increase the rotational force, and head toward the drive outlet 72. In addition, the secondary side impeller 6
3, a part of the fluid sucked from the secondary side inlet 73 due to the rotation is pressurized by the front blade 63B, and the secondary side outlet 7
4, the remaining fluid passes through the communication hole 63DC during the pressurization by the front blade 63B, enters the back blade 63CB, is further pressurized by the back blade 63CB, and is smoothly discharged from the outer peripheral side. The flow path resistance in the side impeller 63 is greatly reduced. Here, since one end of the communication hole is opened in the middle of the flow path of the front blade, the drive blade 61 has the front blade 61B.
The performance of the secondary side impeller 63 is improved by performing the action of the two-stage turbine at the confluence of the side and the communication hole 61DC.
The fluid whose pressure is increased by the front blade 63B flows into the inlet of the back blade 63B, and the back blade 63CC acts as a two-stage pump to increase the discharge pressure of the pump, that is, the operation in which the pump head is increased.
In particular, the power transmission members 67, 68 become large and the back blade 61
When a sufficient installation space for CC and 63CC cannot be secured, it is effective as a means for improving the characteristics of the back blade to balance the characteristics of the front blade and the back blade.

As described above, according to the sixth embodiment of the present invention, the same effect as that of the first embodiment of FIG. 1 can be obtained, and an impeller having higher performance with improved characteristics of the back blade can be obtained. There is an effect that it can be realized.

Further, it is possible to provide a back blade having excellent characteristics even when the installation space for the back blade is small.
There is an effect that the performance balance with the front blade is excellent.

[0087]

As is apparent from the above description, the impeller of the present invention has the front blade of one side open type provided on one side of the blade base and the back blade of one side open type on the other side of the blade base. Since it has a power transmission body and has a communication hole that connects the front and back blades, it reduces mechanical frictional resistance due to axial thrust force and suppresses disc friction loss, which is fluid frictional resistance. Then, there is an effect that the efficiency of the impeller can be improved.

Further, the double-sided blade and the single-sided outflow / inlet configuration have the effect of realizing cost reduction and downsizing, and further improve the degree of freedom in designing the front and back blades and optimize the front and back blades. There is an effect that efficiency can be improved.

Further, in the fluid drive system of the second invention, the drive impeller and the secondary side impeller are separated by the partition wall and connected by the power transmission means, and the drive or secondary side impeller is provided on both sides of the blade base. The front and back blades are communicated with each other through a communication hole, and a power transmission body is provided on one surface of the blade base portion on the partition wall side.

Therefore, the load of driving fluid power on the primary side can be reduced by the high-efficiency impeller having a small resistance loss in which the mechanical frictional resistance at the bearing portion is reduced and the fluid frictional resistance such as the disk frictional loss is also reduced. There is an effect that a compact fluid drive device can be realized.

Further, the impeller having a small loss can increase the capacity of the secondary side even with a limited drive fluid power on the primary side, and can be used in a wide range of applications and a wide range of applications, thereby improving the practicality.

Further, in the impeller of the third invention, the power transmission body is provided on the outer peripheral side of the back blade, and the communication holes are provided on the inner peripheral side and the outer peripheral side of the back blade. It is possible to realize an impeller with a large power transmission capacity and a large torque transmission torque of the rotational force.In addition, the communication hole on the outer peripheral side allows the driving impeller to operate with a higher driving force and the secondary side blade. In vehicles, there is an effect that fluid loss can be reduced and efficiency can be improved.

Further, in the impeller of the fourth invention, the power transmission body is provided on the outer peripheral side of the back blade, and the power transmission body is provided with the concave groove portion extending to the outer peripheral side and the inner peripheral side. Has the effect that the drive impeller receives fluid force, the secondary side impeller reduces fluid pressurization and discharge flow resistance, and the drive impeller can operate with higher drive force.
The secondary side impeller has the effect of increasing the pump head and reducing the flow resistance, and in either case, there is the effect of further increasing efficiency and improving performance.

In the impeller of the fifth invention, the power transmission body is provided on the inner peripheral side of the back blade and the communication hole is provided on the outer peripheral side of the power transmission body. There is an effect that the control response of the change is excellent, and there is an effect that the power loss can be reduced and the performance of the back blade can be improved.

Further, in the impeller of the sixth invention, one end of the communication hole is opened in the middle of the flow path of the front blade and the other end is opened to the inner peripheral side of the back blade for communication, and the back blade has a small installation space. However, in the drive impeller, the performance is improved by the action of the two-stage turbine at the confluence, and in the secondary side impeller, the back vane acts as a two-stage pump to increase the pump head, so the performance of the back vane can be improved. Therefore, even under the constraint that the installation space for the back blade is small, a back blade with excellent characteristics can be provided, and there is an effect that the performance balance with the front blade is excellent.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of an impeller and a fluid drive device according to first and second embodiments of the present invention.

FIG. 2 is a plan view of front blades of the drive impeller and the secondary side impeller of FIG.

FIG. 3 is a plan view of back blades of the drive impeller and the secondary side impeller of FIG.

4 is a sectional view of the impeller of FIG. 2 taken along the line AA.

FIG. 5 is a plan view of the driving impeller and the back blade of the secondary side impeller according to another embodiment of FIG.

FIG. 6 is a sectional view of an impeller and a fluid drive unit according to a third embodiment of the present invention.

7 is a plan view of front blades of the drive impeller and the secondary side impeller of FIG.

8 is a plan view of the drive impeller and the back blade of the secondary side impeller of FIG. 6;

FIG. 9 is a sectional view of an impeller and a fluid drive unit according to a fourth embodiment of the present invention.

FIG. 10 is a plan view of the driving-side and driven-side power transmission bodies of FIG. 9;

11 is a side view of the power transmission body shown in FIG.

FIG. 12 is a plan view of driving-side and driven-side power transmission bodies according to a fourth embodiment of the present invention.

FIG. 13 is a sectional view of an impeller and a fluid drive system according to a fifth embodiment of the present invention.

FIG. 14 is a sectional view of an impeller and a fluid drive unit according to a sixth embodiment of the present invention.

FIG. 15 is a configuration diagram of a conventional pump using a fluid as a drive source.

FIG. 16 is a block diagram of another conventional pump using a fluid as a drive source.

[Fig. 17] System configuration diagram of a conventional central hot water supply and heating system for a residential building

FIG. 18 is a configuration diagram of a conventional pump that uses an electric motor as a drive source.

FIG. 19 is a block diagram of a conventional pump having both suction impellers.

[Explanation of symbols]

 61 Drive impeller 63 Secondary side impeller 65 Partition wall 66 Power transmission means 67 68 Power transmission body 61A, 63A Blade base 61B, 63B Front blade 61C, 63C Back blade 61D, 63D Communication hole

Claims (6)

[Claims] 1. A single-sided open type front blade provided on one side of a blade base, a single-sided open type back blade and a power transmission body provided on the other side of the blade base, the front blade side and the front side. An impeller provided with a communication hole that communicates with the back blade side. 2. A drive impeller that uses a primary fluid as a drive source of rotational force, a secondary impeller that circulates a secondary fluid, and the primary fluid and the secondary fluid that are hermetically separated from each other. A partition wall, a power transmission unit in which a drive-side power transmission body provided in the drive impeller and a driven-side power transmission body provided in the secondary-side impeller are opposed to each other through the partition wall, and the drive A front surface of a single-sided open type provided on at least one of the impeller or the secondary side impeller and one side of the blade base, and a single-sided open type back blade and a power transmission body provided on the other side of the blade base. A fluid drive device equipped with an impeller having a communication hole that connects the front blade side and the back blade side. 3. The impeller according to claim 1, wherein the power transmission body is provided on an outer peripheral side of the back blade, and the communication holes are provided on an inner peripheral side and an outer peripheral side of the back blade. 4. The impeller according to claim 1, wherein the power transmission body is provided on an outer peripheral side of the back blade, and a concave groove portion is provided extending to an outer peripheral side and an inner peripheral side of the power transmission body. 5. The impeller according to claim 1, wherein the power transmission body is provided on the inner peripheral side of the back blade, and the communication hole is provided on the outer peripheral side of the power transmission body. 6. The impeller according to claim 1, wherein the communication hole communicates with the middle of the flow path of the front blade and the inner peripheral side of the back blade.