Full-Circumferential Flow Pump

1. Field of the Invention

The present invention relates to a full-circumferential flow pump and, more particularly, to a full-circumferential flow pump which has a motor, an outer cylindrical pump casing enclosing the motor, and an annular space formed between a motor frame barrel provided around a stator of the motor and the outer cylindrical pump casing.

2. Description of the Related Art

It has been customary to press sheet steel such as stainless steel to form a pump casing according to a deep drawing process, and then weld or otherwise fasten a suction or discharge flange to the pressed pump casing. The pump casing thus fabricated is liable to be deformed due to the internal pressure developed in the pump casing itself and also external forces applied to the pump casing from piping connected thereto. Any deformation that the pump casing suffers should be reduced to such a level that the pump casing will never be in contact with an impeller housed in the pump casing. Therefore, the pressed pump casing must meet mechanical strength requirements for bearing loads including external forces applied from the connected piping and internal pressure developed in the pump casing, and also rigidity requirements for maintaining a desired clearance between a liner ring and the impeller.

Inasmuch as the pressed pump casing is of a relatively flexible structure with respect to applied loads, it is impossible for the pressed pump casing itself to satisfy both the mechanical strength requirements and the rigidity requirements. To achieve a desired level of rigidity, conventional pressed pump casings have employed a steel sheet having a thickness greater than the thickness required to withstand an internal pressure developed therein, or a reinforcing member of complex shape attached thereto.

As described above, conventionally, in order to prevent the pump casing or the liner portion thereof from being deformed, the rigidity of the pump casing has been increased by employing either a steel sheet having a thickness greater than the thickness required to withstand an internal pressure developed in the pump casing or a reinforcing member of complex shape attached thereto. The steel sheet of increased thickness is, however, difficult to press to shape, and the reinforcing member of complex shape results in an increase in the cost of manufacture of the pump casing.

It is therefore an object of the present invention to provide a full-circumferential flow pump having a pump casing which has a liner portion which is prevented from being deformed, and which is made of a metal sheet having a thickness not greater than that necessary to withstand external forces applied to the pump casing and an internal pressure developed in the pump casing, and which has no reinforcing member for reinforcing the pump casing.

According to an aspect of the present invention, there is provided a full-circumferential flow pump comprising: a motor having a stator, a rotor mounted on a shaft and disposed in the stator for rotation relative to the stator and an outer frame barrel enclosing the stator; an outer cylindrical pump casing disposed around the outer frame barrel with an annular space defined therebetween; a pump assembly having at least one impeller mounted on an end of the shaft for pumping a fluid into the annular space or pumping a fluid from the annular space; an inner casing provided in the outer cylindrical pump casing for accommodating the impeller; and a resilient seal disposed between the outer cylindrical pump casing and the inner casing for preventing a pumped fluid in the outer cylindrical pump casing from leaking towards a suction side of the impeller.

According to the present invention, the inner casing is housed in the outer cylindrical pump casing and spaced therefrom by the resilient seal interposed between the inner casing and the outer cylindrical pump casing. The resilient seal is effective to absorb deformations of the outer cylindrical pump casing due to external forces applied thereto. Hence, such deformations of the outer cylindrical pump casing are not transmitted to the inner casing. The inner casing is thus prevented from being deformed under pressure. Since the outer cylindrical pump casing is not required to be excessively rigid, the outer cylindrical pump casing is not required to have a thickness greater than that necessary to withstand the internal pressure developed in the pump casing, and is not required to be reinforced by a special reinforcing member. With the inner casing having the liner portion which is prevented from being deformed, it is easy to maintain a clearance between the liner portion and the impeller. The inner casing may also be of a reduced thickness as it is free from loads due to external forces. Consequently, the inner casing may also be easily pressed to shape with high accuracy.

According to one aspect of the present invention, since the inner casing is supported by the canned motor in a spaced relationship to the outer cylindrical pump casing, vibration and noise of the canned motor are not transmitted to the outer cylindrical pump casing through the inner casing. This structure of the pump casing is suitable for prevention of propagation of vibration and noise of the canned motor.

According to another aspect of the present invention, the inner casing is spaced from all components which constitute a pump casing separating internal surroundings in which a fluid to be pumped is contained, from external surroundings. Thus, even if external forces including an impact force are applied to the outer cylindrical pump casing, the resilient seal is effective to absorb deformations of the outer cylindrical pump casing. Hence, such deformations of the outer cylindrical pump casing are not transmitted to the inner casing. With the inner casing having the liner portion, it is easy to maintain a clearance between the liner portion and the impeller. Further, vibration and noise of the canned motor are not transmitted to the outer cylindrical pump casing through the inner casing.

The above and other objects, features, and advantages of the present invention will become apparent from the following description when taken in conjunction with the accompanying drawings which illustrate preferred embodiments of the present invention by way of example.

FIG. 1 is a cross-sectional view of a full-circumferential flow pump according to a first embodiment of the present invention;

FIG. 2 is a cross-sectional view taken along line II--II of FIG. 1;

FIG. 3 is a cross-sectional view of a full-circumferential flow pump according to a second embodiment of the present invention; and

FIG. 4 is a cross-sectional view taken along line IV--IV of FIG. 3.

A full-circumferential flow pump according to the first embodiment of the present invention is shown in FIGS. 1 and 2. As shown in FIG. 1, the full-circumferential flow pump is of the double-suction type and has a canned motor 6 disposed centrally therein. The canned motor 6 includes a shaft 7 having opposite ends on which there are fixedly mounted respective pairs of impellers 8A, 9A and 8B, 9B each having an axially outwardly open suction mouth. Thus, two pump assemblies are disposed respectively on opposite sides of the canned motor 6. The canned motor 6 and the impellers 8A, 9A, 8B and 9B are housed in a pump casing 1 comprising an outer cylindrical pump casing 2 and a pair of spaced end covers 63 and 63. The end covers 63 are detachably fastened to the respective axial ends of the outer cylindrical pump casing 2 by respective flanges 51 and 52. The outer cylindrical pump casing 2 and the end covers 63 are made of sheet metal. The impellers 8A, 9A, 8B and 9B have blades made of sheet metal.

The canned motor 6 comprises a stator 13, a substantially cylindrical outer frame barrel 14 which encloses the stator 13, a pair of axially spaced side frame members 15 and 16 attached respectively to axial open ends of the outer frame barrel 14, and a cylindrical can 17 which is fitted in the stator 13 and welded to the side frame members 15 and 16. A rotor 18 which is rotatably housed in the stator 13 is supported on the shaft 7. An annular space or annular fluid passage 40 is defined between the outer frame barrel 14 and the outer cylindrical pump casing 2. A terminal case 20 is welded to the outer frame barrel 14. The canned motor 6 and the outer cylindrical pump casing 2 are fixed to each other by the terminal case 20 and stays 43 interposed therebetween. A case 77 is welded to the outer cylindrical pump casing 2 to house a frequency converter 76 therein. Leads extend outwardly from motor coils in the outer frame barrel 14 through the terminal case 20 and are electrically connected to the frequency converter 76.

The outer cylindrical pump casing 2 has a pair of suction windows 2a and 2b defined therein near the respective axial ends, and a suction case 55 is mounted on an outer circumferential surface of the outer cylindrical pump casing 2 so as to connect the suction windows 2a and 2b to each other. The suction case 55 is a substantially rectangular cup-shaped case having a bottom on one end and an opening on the other end. The suction case 55 is formed with a suction opening 55a for introducing a fluid therethrough. A suction nozzle 56 with a suction port 56a defined therein is fixedly mounted on the suction case 55 around the suction opening 55a. A suction flange 57 is mounted on the suction nozzle 56.

As shown in FIG. 1, two axially spaced inner casings 65 are disposed in the outer cylindrical pump casing 2 to house the respective pairs of impellers 8A, 9A and 8B, 9B. The inner casings 65 comprise a cylindrical member 65a and a cover 65b which covers an open end of the cylindrical member 65a, respectively, and are in the form of a cylindrical receptacle. The inner casings 65 have respective axial openings in which respective seal members 75 of a resilient material such as rubber are secured, and include respective bottoms with suction openings 65c defined respectively therein.

The seal members 75 serve to prevent a pumped fluid discharged from the impellers 9A and 9B from leaking toward the suction-side of the impellers 8A and 8B, respectively. The inner casings 65 are fixed to the side frame members 15 and 16 by bolts 66, respectively. In each of the inner casings 65, there are provided two retainers 46 having respective liner rings 45, a return blade 47 for guiding a fluid from the first-stage impeller 8A or 8B to the second-stage impeller 9A or 9B, and a guide device 48 for guiding a fluid discharged from the second-stage impeller 9A or 9B toward the annular space 40.

As shown in FIGS. 1 and 2, the annular space 40 is defined between the outer cylindrical pump casing 2 and the motor frame barrel 14. The outer cylindrical pump casing 2 has a discharge opening 2c defined in its circumferential wall and held in communication with the annular space 40. A discharge nozzle 68 with a discharge port 68a defined therein is fixedly mounted on the outer cylindrical pump casing 2 around the discharge opening 2c, and a discharge flange 69 is fixedly mounted on the discharge nozzle 68.

A bearing housing 21 is detachably fixed to the side frame member 16 with a resilient O-ring 29 being interposed between the bearing housing 21 and the side frame member 16. The bearing housing 21 and the side frame member 16 are joined to each other by a socket-and-spigot joint with a clearance fit with the O-ring 29 disposed therein. The bearing housing 21 is also prevented from being axially dislodged from the side frame member 16 by a plate fixed to the side frame member 16. A resilient member 30 such as rubber is disposed in an axial gap between the bearing housing 21 and the side frame member 16. The bearing housing 21 supports a radial bearing 22 on its radially inner surface and a stationary thrust bearing 23 on its axially outer surface. A shaft sleeve 31 fitted over the shaft 7 is rotatably supported by the radial bearing 22.

Two thrust disks 26 and 27 are fixedly mounted on the shaft 7 for axially sandwiching the bearing housing 21. The thrust disk 26 holds a thrust bearing 24 rotatable with the shaft 7 and facing an axially outer end surface of the stationary thrust bearing 23. The thrust disk 27 holds a thrust bearing 25 rotatable with the shaft 7 and facing an axially inner end surface of the radial bearing 22 which provides a stationary thrust sliding surface.

A bearing housing 32 is detachably fixed to the side frame member 15 with a resilient O-ring 37 being interposed between the bearing housing 32 and the side frame member 15. The bearing housing 32 holds a radial bearing 33 on the radially inner end. A shaft sleeve 34 fitted over the shaft 7 is rotatably supported by the radial bearing 33. The sleeve 34 contacts a washer 35 which is fixed to the shaft 7 through the impeller 9A, a sleeve 42 and the impeller 8A by double nuts 36.

Operation of the full-circumferential flow double-suction pump in FIGS. 1 and 2 will be described below.

The fluid which is drawn in through the suction port 56a and the suction opening 55a is divided by the suction case 55 into two fluid flows which are introduced into the pump assemblies through the suction windows 2a and 2b. The fluid flows pass through the suction openings 65c into the inner casings 65, and then are introduced to the impellers 8A and 8B, respectively. The fluid discharged from the impellers 8A and 8B flows to the impellers 9A and 9B, respectively. The fluid discharged from the impellers 9A and 9B is guided by the guide devices 48 and introduced into the annular space or passage 40 defined between the outer cylindrical pump casing 2 and the motor frame barrel 14. The fluid flows passing through the annular passage 40 merge in the middle of the annular passage 40, and then are discharged through the discharge opening 2c of the outer cylindrical pump casing 2 and the discharge nozzle 68 from the discharge port 68a.

In the above embodiment, the outer cylindrical pump casing 2 and the inner casings 65 are sealed from each other by the seal members 75 across which the differential pressure between the suction and discharge pressures is applied. Since the seal members 75 are effective to absorb deformations of the outer cylindrical pump casing 2, such deformations of the outer cylindrical pump casing 2 are not transmitted to the inner casings 65. Therefore, each of the inner casings 65 is not substantially deformed, and a clearance is maintained between each of the liner rings 45 and each of the impellers 8A, 8B, 9A and 9B for keeping each of the liner rings 45 out of contact with each of the impellers 8A, 8B, 9A and 9B.

Since the inner casings 65 are supported by the canned motor 6 in a spaced relationship to the outer cylindrical pump casing 2 and the covers 63, vibration and noise of the canned motor 6 is not transmitted to the outer cylindrical pump casing 2 and the covers 63 through the inner casings 65. This structure of the pump casing is suitable for prevention of propagation of vibration and noise of the canned motor 6.

FIGS. 3 and 4 show a full-circumferential flow pump according to the second embodiment of the present invention. The full-circumferential flow pump according to the second embodiment is of the double-suction type and is essentially the same as the full-circumferential flow pump according to the first embodiment which is illustrated in FIGS. 1 and 2. Those parts shown in FIGS. 3 and 4 which are identical to those shown in FIGS. 1 and 2 are denoted by identical reference numerals, and will not be described in detail below.

According to the second embodiment, as shown in FIGS. 3 and 4, the full-circumferential flow pump has a canned motor 6 disposed centrally therein. The canned motor 6 includes a shaft 7 having opposite ends on which there are fixedly mounted respective pairs of impellers 8C, 9C and 8D, 9D each having an axially inwardly open suction mouth. Thus, two pump assemblies are disposed respectively on opposite sides of the canned motor 6. The canned motor 6 and the impellers 8C, 9C and 8D, 9D are housed in a pump casing 1 comprising an outer cylindrical pump casing 2 made of sheet metal and a pair of spaced end covers 63 made of sheet metal. The end covers 63 are detachably fastened to respective axial ends of the outer cylindrical pump casing 2 by respective flanges 51 and 52. The impellers 8C, 9C and 8D, 9D have blades made of sheet metal.

The canned motor 6 has substantially the same structure as that of the first embodiment of FIG. 1, but additionally has guide members 80 which are attached to the side frame members 15 and 16, respectively and have a radial flow passage. Inner casings 85 housing the impellers 8C, 9C and 8D, 9D comprise an integral cylindrical-cup shaped member, respectively. The inner casings 85 are fitted over the guide members 80, respectively. The inner casings 85 have respective axial openings in which respective seal members 75 of a resilient material such as rubber are secured, and include respective bottoms with discharge openings 85a defined respectively therein. The seal members 75 serve to prevent a pumped fluid discharged from the impellers 9C and 9D from leaking toward the suction-side of the impellers 8C and 8D, respectively. A stay 87 is interposed between each of the inner casings 85 and each of the covers 63. A resilient material 88 made of sheet-like rubber is interposed between the stay 87 and the cover 63. In each of the inner casings 85, there are provided two retainers 46 having respective liner rings 45, a return blade 47 for guiding a fluid from the first-stage impeller 8C or 8D to the second-stage impeller 9C or 9D, and a return blade 48 for guiding a fluid discharged from the second-stage impeller 9C or 9D toward the discharge opening 85a. The outer cylindrical pump casing 2 has a suction opening 2e at the central portion thereof, and a suction nozzle 89 with a suction port 89a fixedly mounted on the outer cylindrical pump casing 2 around the suction opening 2e. A suction flange 90 is fixedly mounted on the suction nozzle 89.

The outer cylindrical pump casing 2 has a pair of discharge windows 2f and 2g defined therein near the respective axial ends, and a discharge case 91 is mounted on an outer circumferential surface of the outer cylindrical pump casing 2 so as to connect the discharge windows 2f and 2g to each other. The discharge case 91 is a substantially rectangular cup-shaped case having a bottom on one end and an opening on the other end. The discharge case 91 is formed with a discharge opening 91a. A discharge nozzle 92 with a discharge port 92a defined therein is fixedly mounted on the discharge case 91 around the discharge opening 91a. A discharge flange 93 is mounted on the discharge nozzle 92. Other components of the pump in FIGS. 3 and 4 are the same as those of the pump in FIGS. 1 and 2.

Operation of the full-circumferential flow double-suction pump in FIGS. 3 and 4 will be described below.

The fluid which is drawn in through the suction opening 2e is divided by the annular passage 40 into two fluid flows which are introduced into the pump assemblies through the guide members 80. The fluid flows passing through the guide members 80 are introduced into the impellers 8C and 8D, respectively. The fluid discharged from the impellers 8C and 8D flows into the impellers 9C and 9D through the return blades 47, respectively. The fluid discharged from the impellers 9C and 9D passes through the return blades 48 and then flows through the openings 85a of the inner casings 85 and the discharge windows 2f and 2g into the discharge case 91. The fluid flows which have passed through the discharge windows 2f and 2g merge in the discharge case 91. Thereafter, the fluid is discharged through the discharge opening 91a of the discharge case 91 from the discharge port 92a of the discharge nozzle 92.

In the above embodiment, the outer cylindrical pump casing 2 and the inner casings 85 are sealed from each other by the seal members 75 across which the differential pressure between the suction and discharge pressures is applied. Since the seal members 75 are effective to absorb deformations of the outer cylindrical pump casing 2, such deformations of the outer cylindrical pump casing 2 are not transmitted to the inner casings 85. Therefore, each of the inner casings 85 is not substantially deformed, and a clearance is maintained between each of the liner rings 45 and each of the impellers 8C, 8D, 9C and 9D for keeping each of the liner rings 45 out of contact with each of the impellers 8C, 8D, 9C and 9D.

Since the inner casings 85 do not contact the outer cylindrical pump casing 2 and the covers 63 directly due to the presence of the seal members 75 and the resilient materials 88, vibration and noise of the canned motor 6 is not transmitted to the outer cylindrical pump casing 2 and the covers 63 through the inner casings 65. This structure of the pump casing is suitable for prevention of propagation of vibration and noise of the canned motor 6.

According to the present invention, the outer cylindrical pump casing is not required to be excessively rigid, the outer cylindrical pump casing is not required to have a thickness greater than that necessary to withstand the internal pressure developed in the pump casing, and is not required to be reinforced by a special reinforcing member. Therefore, it is easy to press form the pump casing to shape, thus improving production of the pump casing while maintaining a relatively small number of parts of the pump casing.

According to the present invention, since the inner casing for accommodating the guide device is provided, the shape of the outer cylindrical pump casing is not influenced by the guide device for obtaining a desired hydrodynamic performance, thus enabling the outer cylindrical pump casing to be a simple structure. Further, it is not necessary to ensure concentricity of the outer cylindrical pump casing and to very accurately machine the outer cylindrical pump casing.

According to the present invention, the inner casing may also be of a small thickness as it is free from loads due to external forces. Consequently, the inner casing may be also easily pressed to shape with high accuracy and may be made of plastics.

Although certain preferred embodiments of the present invention have been shown and described in detail, it should be understood that various changes and modifications may be made therein without departing from the scope of the appended claims.