the canned pump including a doubled - sided - supported stationary shaft without any monitor device as shown in fig1 a and 3 a with reference to fig1 a , 3 a , fig1 a is a cross - sectional view of a double - sided - supported stationary shaft without any monitor device of the canned pump according to the present invention , and fig3 a is a cross - sectional view of a containment shell of a double - sided - supported stationary shaft of the canned pump according to the present invention . the canned pump comprises : a pump casing 4 , a triangle front support 31 , a type i impeller 5 , a type i containment shell 41 , a stationary shaft 3 and a canned motor 8 . the pump casing 4 includes an inlet 44 , an outlet 45 and a flow channel 47 , and is used for containing the type i impeller 5 . a front thrust ring 46 , installed on an inner side of the inlet 44 of the pump casing 4 , is used for mating with a thrust bearing 53 of the type i impeller 5 to form an axial thrust bearing together . the triangle front support 31 , fixed with the inlet 44 of the pump casing 4 , passes through a hub aperture 54 axially for supporting an end of the stationary shaft 3 . the type i impeller 5 is assembled in the pump casing 4 . the triangle front support 31 may pass through the hub aperture 54 axially and is used for supporting the end of the stationary shaft 3 . a hub plate 52 is used for combining an axially extended part 76 of an inner rotor 7 of the canned motor 8 so that the type i impeller 5 and the inner rotor 7 are integrated into one piece or embedded to be combined into one piece . the type i containment shell 41 is a cup - shaped shell structure with a blank rear shaft support 413 installed on a bottom side of the type i containment shell 41 . there is no any through hole on the blank rear shaft support 413 with a ring slot 413 b for ensuring there is no leakage from the type i containment shell 41 . a shell flange part 411 , installed on a front side of the type i containment shell 41 , is combined with the pump casing 4 and a pump side flange 811 of the canned motor 8 for preventing a corrosive fluid from leakage . a shell column part 412 , installed on a lateral side of the type i containment shell 41 , passes through the inner side of a stator 83 with a loose slide fit . a motor rear casing 82 of the canned motor 8 is tightly attached on the bottom side of the type i containment shell 41 with sufficient supporting strength . the blank rear shaft support 413 is installed at the center of the bottom side of the type i containment shell 41 and extends inwardly and axially to an inner space of a rotor yoke 72 . the blank rear shaft support 413 includes a shaft hold hole 413 a protruding inwardly and positioned in the blank rear shaft support 413 , and includes a ring slot 413 b installed on the outer side of the blank rear shaft support 413 . a rear thrust ring 414 is installed on front surface of the shaft hold hole 413 a and is used for mating with a ceramic bearing 79 of the inner rotor 7 to form the axial thrust bearing . an outer sidewall surface of the shaft hold hole 413 a is completely combined with and supported by a shaft metal rear support 821 a of the motor rear casing 82 , and a bottom side of the shaft hold hole 413 a is completely fitted with the inner side of a backward bulged part 823 of the motor rear casing 82 , and the length of the bulged part 823 is fitted with the depth h of the shaft hold hole 413 a for providing the high - stiff support for the stationary shaft 3 , and hereafter this kind of structure is called a metal holding support . the type i containment shell 41 is only used for providing anti - corrosion isolating property without providing stiff support for the stationary shaft 3 . the stationary shaft 3 , which is a double - sided supported structure , is made of a ceramic material with anti - corrosion and anti - wear properties . a front side of the stationary shaft 3 is supported by the triangle front support 31 and a rear side of the stationary shaft 3 is supported by the blank rear shaft support 413 which extends outwardly . a center portion of the stationary shaft 3 mates with the ceramic bearing 79 for supporting the rotation of the inner rotor 7 , and the length of the center portion of the stationary shaft 3 satisfies the length of ceramic bearing 79 so that the length of the center portion is favorable for withstanding a composite force which is borne by the inner rotor 7 and reserving an axial free - movement space for the inner rotor 7 . the ring slot 413 b of the blank rear shaft support 413 is tightly combined with and supported by the shaft metal rear support 821 a of the motor rear casing 82 and provides a hold length l . moreover , the ring slot 413 b may overcome the problem of the reduced strength of plastic material due to the rise of the temperature . the canned motor 8 comprises the stator 83 , a motor casing 81 , a motor rear casing 82 and the inner rotor 7 . the stator 83 is tightly fixed in the motor casing 81 . windings 831 are winded on the stator 83 . a pwm electric power , applied on the windings 831 , generates a magnetic flux to interact with a magnetic field of the inner rotor 7 , the inner rotor 7 generates torque and rotates to drive the type i impeller 5 to output hydraulic power . the type i containment shell 41 prevents the windings 831 of the stator 83 from being corroded by the corrosive fluid . the pump side flange 811 of the motor casing 81 is used for tightly fixing with the shell flange part 411 and the pump casing 4 to prevent the leakage from the corrosive fluid . a back flange of the motor casing 81 is used for fixing the motor rear casing 82 to provide a complete structure support so that the shaft metal rear support 821 a of the motor rear casing 82 may provide support needed by the stationary shaft 3 . the motor rear casing 82 is fixed with the back flange of the motor casing 81 so that the shaft metal rear support 821 a of the motor rear casing 82 may provide support needed by the stationary shaft 3 . an electric power wire of the windings 831 of the stator 83 is connected to a drive power via a lead port 822 . the inner rotor 7 is a ring - shaped structure comprising main magnets 71 , the rotor yoke 72 and the axially extended part 76 and forming a ring - shaped rotor resin enclosure 74 covered with an engineering plastic with anti - corrosion property . a ceramic bearing 79 is installed in a central hole of the inner rotor 7 . the hub plate 52 is used for combining with the axially extended part 76 of the inner rotor 7 so that the type i impeller 5 and the inner rotor 7 are integrated into one piece or embedded to be combined with each other into one piece . when the pump operates , fluid flows along an inlet streamline 6 and is pressurized after flowing through the type i impeller 5 , such as an impeller exit streamline 61 . the pressurized fluid is output by an outlet 45 and a portion of the fluid , such as a turn back streamline 62 , enters the inner space 415 of the type i containment shell 41 via a rear side of the type i impeller 5 . after that , the fluid flows to the gap between an outer side of the inner rotor 7 and the inner space 415 of the type i containment shell 41 , continuing through another gap between the stationary shaft 3 and the ceramic bearing 79 . then , the fluid flows through the hub aperture 54 , such as an end lubrication streamline 65 , to an inlet of the type i impeller 5 . the circulating flowing of the fluid is used for providing the lubrication for the ceramic bearing 79 and taking away the heat generated by the inner rotor 7 . the canned pump including a singled - sided - supported cantilever composited stationary shaft without any monitor device which is shown as in fig1 c , fig3 b and fig5 b with reference to fig1 c and fig3 b , fig1 ac is a cross - sectional view of a single - sided - supported cantilever composited stationary shaft without any monitor device of the canned pump according to the present invention , fig3 b is a cross - sectional view of a containment shell of a cantilever stationary shaft of the canned pump according to the present invention , and fig5 b shows an inner rotor bearing multiple forces and moments thereof on a single - sided - supported cantilever stationary shaft according to the present invention . the canned pump comprises a metal casing 4 a , a type ii impeller 5 a , a type ii containment shell 41 a , a composited stationary shaft 3 a and a canned motor 8 . the metal casing 4 a which includes an inlet 44 , an outlet 45 and a flow channel 47 is used for containing the type ii impeller 5 a . the metal casing 4 a is a metal wok structure by casting . a casing liner 4 b , made of anti - corrosive plastic , is covered on an inner side of the metal casing 4 a . a front thrust ring 46 , installed at the inlet 44 in an inner side of the metal casing 4 a , is used for mating with a thrust bearing 53 of the type ii impeller 5 a to form an axial thrust bearing . the type ii impeller 5 a is installed in the metal casing 4 a . a hub plate 52 is used for being combined with an axially extended part 76 of an inner rotor 7 so that the type ii impeller 5 a and the inner rotor 7 are integrated into one piece or embedded with each other into one piece . a hub balance hole 54 a is a aperture at the center of a curve hub plate 55 for making circulating fluid re - circulate , for example , an end lubrication streamline 65 . the inlet 44 of the metal casing 4 a and the inlet of the type ii impeller 5 a form a smooth and increasing - inner - diameter channel without any disturbance , and the shape of the curve hub plate 55 is smooth curve shape as well . therefore , it is favorable for reducing the flow speed of the fluid to make sure the pump has good npshr ability . the type ii containment shell 41 a is a cup - shaped structure which has a rear shaft seat 418 including a hole installed on a bottom side of the type ii containment shell 41 a . a shell flange part 411 , installed on a front side of the type ii containment shell 41 a , is combined with the metal casing 4 a and a pump side flange 811 of the canned motor 8 , which prevents the fluid from leakage . a shell column part 412 , installed on a lateral side of the type ii containment shell 41 a , passes through the inner side of the stator 83 with a loose slide fit . also , the bottom side of the type ii containment shell 41 a is tightly attached to the motor rear casing 82 with sufficient supporting strength . the rear shaft seat 418 , installed on the center on the bottom side of the type ii containment shell 41 a , extends inwardly towards the inner space of the rotor yoke 72 , and the rear shaft seat 418 further protrudes inwardly and includes an aperture 418 a installed at an inner side of the rear shaft seat 418 and a concave aperture 418 b installed on an outer side of the rear shaft seat 418 corresponding to each other , and the aperture , installed on the center of the rear shaft seat 418 , is used for containing the composited stationary shaft 3 a , and a seal surface 418 d of the rear shaft seat 418 is tightly attached by a surface of a ceramic shaft sleeve 33 including an o ring and a shaft metal rear support 821 a of the motor rear casing 82 , and hereafter this kind of structure is called metal composited support , which may make sure that there is no leakage . this embodiment does not have any monitor device to provide a detection device for detecting the wear of the bearing . the composited stationary shaft 3 a , which is a cantilever supported structure , is made of a ceramic shaft sleeve 33 , a metal shaft 32 and a motor rear casing 82 with anti - corrosion and anti - wear properties . the composited stationary shaft 3 a and the type ii containment shell 41 a form a completely sealed shaft system . when an end of the composited stationary shaft 3 a is installed on a composited shaft metal rear support 821 c of the motor rear casing 82 , a required supporting strength is provided . the metal shaft 32 passes through a sleeve central hole 332 of the ceramic shaft sleeve 33 , and includes a circular head 321 which is installed at an end of the metal shaft 32 and pressed tightly against a front end surface 333 of the ceramic shaft sleeve 33 . a teeth part 323 of the metal shaft 32 passes through the rear shaft seat 418 of the type ii containment shell 41 a and a central hole of the composited shaft metal rear support 821 c which is extended inwardly in a radial direction . a nut of the teeth part 323 is fixed on the motor rear casing 82 a so that a sliding thrust surface 331 of the ceramic shaft sleeve 33 is tightly pressed against a surface of the composited shaft metal rear support 821 c . a circular head 321 of the metal shaft 32 is covered with a resin enclosure 322 , and an o ring is installed on the circular head 321 which is used for sealing and corrosion resistance . the sliding thrust surface 331 of the ceramic shaft sleeve 33 is used for mating with a ceramic bearing 79 of the inner rotor 7 to form an axial thrust bearing . a surface of the sliding thrust surface 331 and a surface of the composited shaft metal rear support 821 c of the motor rear casing 82 a are tightly fixed and compressed with each other and a seal surface 418 d of the rear shaft seat 418 , packed tightly and installed between the sliding thrust surface 331 and the composited shaft metal rear support 821 c is encapsulated by a surface of the sliding thrust surface 331 including another o ring , which makes sure there is no leakage , thereby forming a composited stationary shaft 3 a with high stiffness . the canned motor 8 comprises the stator 83 , a motor casing 81 , a motor rear casing 82 a and an inner rotor 7 . the stator 83 is tightly fixed in the motor casing 81 . windings 831 are winded on the stator 83 . a pwm electric power , applied on the windings 831 , may generate a magnetic flux to interact with a magnetic field of the inner rotor 7 , so the inner rotor 7 generates torque and rotates to drive the type ii impeller 5 a to output hydraulic power . the type ii containment shell 41 a prevents the windings 831 of the stator 83 from being corroded by the corrosive fluid . the pump side flange 811 which is installed on a lateral pump side of the motor casing 81 is used for fixing with the shell flange part 411 and the metal casing 4 a for preventing corrosive fluid from leakage . a back flange of the motor casing 81 is used for fixing with the motor rear casing 82 a to provide a complete structure support so that the composited shaft metal rear support 821 c of the motor rear casing 82 a may provide support which is required by the composited stationary shaft 3 a . the motor rear casing 82 a is tightly fixed with the back flange of the motor casing 81 so that the composited shaft metal rear support 821 c of the motor rear casing 82 a may provide support which is required by the composited stationary shaft 3 a . an electric power wire of the windings 831 of the stator 83 is connected to a drive power via a lead port 822 . the inner rotor 7 is a ring - shaped structure comprising main magnets 71 , a rotor yoke 72 and an axially extended part 76 and forming a ring - shaped rotor resin enclosure 74 which is covered with an engineering plastic with anti - corrosion property . a ceramic bearing 79 is installed in a central hole of the inner rotor 7 . the hub plate 52 is used for combining with the axially extended part 76 of the inner rotor 7 so that the type ii impeller 5 a and the inner rotor 7 are integrated into one piece or embedded to be combined with each other into one piece . when the pump operates , fluid flows along an inlet streamline 6 and is pressurized after flowing through the type ii impeller 5 a , such as an impeller exit streamline 61 . the pressurized fluid is output by an outlet 45 , and a portion of the fluid , such as a turn back streamline 62 , enters the inner space 415 of the type ii containment shell 41 a via a rear side of the type ii impeller 5 a in the mean time . after that , the fluid flows to the gap between an outer side of the inner rotor 7 and the inner space 415 of the type ii containment shell 41 a , continuing through another gap between of the composited stationary shaft 3 a and the ceramic bearing 79 . then , the fluid flows through a hub balance hole 54 a which is installed at the center of the curve hub plate 55 , such as an end lubrication streamline 65 , to an inlet of the type ii impeller 5 a . the circulating flowing of the fluid is used for providing the lubrication for the ceramic bearing 79 and taking away the heat generated by the inner rotor 7 . the canned pump including a doubled - sided - supported cantilever composited stationary shaft and a monitor device shown in fig1 b , 1 e and fig3 a with reference to fig1 b , 1 e and fig3 a , fig1 b is a cross - sectional view of a double - sided supported stationary shaft with a monitor device of the canned pump according to the present invention , fig1 e is a cross - sectional view of a double - sided - supported stationary shaft with a monitor device and with a lengthened bearing of the canned pump according to the present invention , and fig3 a is a cross - sectional view of a containment shell of a double - sided - supported stationary shaft of the canned pump according to the present invention . the canned pump comprises a pump casing 4 , a triangle front support 31 , a type i impeller 5 , a type i containment shell 41 , a monitor device 9 , a stationary shaft 3 and a canned motor 8 . the pump casing 4 includes an inlet 44 , an outlet 45 and a flow channel 47 , and is used for containing the type i impeller 5 . a front thrust ring 46 is installed on an inner side of the inlet 44 of the pump casing 4 and used for mating with a thrust bearing 53 of the type i impeller 5 to form an axial thrust bearing together . the triangle front support 31 is fixed on the inlet 44 of the pump casing 4 , passes through a hub aperture 54 axially and is used for supporting an end of the stationary shaft 3 . the type i impeller 5 is assembled in the pump casing 4 . the triangle front support 31 may pass through the hub aperture 54 axially and is used for supporting the end of the stationary shaft 3 . a hub plate 52 is used for combining an axially extended part 76 of an inner rotor 7 of the canned motor 8 so that the type i impeller 5 and the inner rotor 7 are integrated into one piece or embedded to be combined into one piece . the type i containment shell 41 is a cup - shaped shell structure comprising a blank rear shaft support 413 installed on a bottom side of the type i containment shell 41 . there is no any through hole on the blank rear shaft support 413 with a ring slot 413 b for ensuring there is no leakage from the type i containment shell 41 . a shell flange part 411 , installed on a front side of the type i containment shell 41 , is combined with the pump casing 4 and a pump side flange 811 of the canned motor 8 for preventing a corrosive fluid from leakage . a shell column part 412 , installed on a lateral side of the type i containment shell 41 , passes through in the inner side of a stator 83 with a loose slide fit . a motor rear casing 82 of the canned motor 8 is tightly attached on the bottom side of the type i containment shell 41 with sufficient support strength . the blank rear shaft support 413 is installed at the center of the bottom side of the type i containment shell 41 and extends inwardly and axially to an inner space of a rotor yoke 72 . the blank rear shaft support 413 includes a center shaft hold hole 413 a protruding inwardly , and the ring slot 413 b is on the outer side of the blank rear shaft support 413 . a rear thrust ring 414 is installed on front surface of the shaft hold hole 413 a and is used for mating with a ceramic bearing 79 of the inner rotor 7 to form an axial thrust bearing . the monitor set 93 , which includes a secondary yoke 91 and multiple signal coil pairs 92 , is installed on the monitoring shaft metal rear support 821 b of the motor rear casing 82 , and put into the ring slot 413 b of outer sidewall surface of the shaft hold hole 413 a . a bottom side of the blank rear shaft support 413 is completely fitted with the inner side of a bulged part 823 of the motor rear casing 82 . the length of the bulged part 823 is fitted with the depth h of the shaft hold hole 413 a for providing the high - stiff support of the stationary shaft 3 . the type i containment shell 41 is only used for providing anti - corrosion isolating ability without providing stiff support for the stationary shaft 3 . the monitor device 9 , positioned in the ring slot 413 b of the blank rear shaft support 413 which extends axially , is used for detecting the wear of the bearing . the structure of the monitor device 9 comprises multiple secondary magnets 73 and a monitor set 93 . the number of the secondary magnets 73 is the same as the main magnets 71 . the secondary magnets 73 are assembled at one end of the inner side of a rotor yoke 72 of the inner rotor 7 in the vicinity of the bottom side of the type i containment shell 41 as well as face oppositely away from the main magnets 71 . the axial length of the secondary magnets 73 is at least more than twice as great as the length of an axial movement ( including the axial wear of the bearing ) of the inner rotor 7 . the monitor set 93 comprises the secondary yoke 91 ( not shown ) and the multiple signal coil pairs 92 . the secondary yoke 91 take the position at the center of the secondary magnets 73 as a reference point , the axial length of the secondary yoke 91 is divided into two sections , a front section and a rear section . when the secondary magnets 73 are moved axially , both ends of the secondary magnets 73 do not exceed the ranges of the two sections of the secondary yoke 91 . the stationary shaft 3 is the doubled - sided supported structure made of ceramic material with anti - corrosion and anti - wear properties . a front side of the stationary shaft 3 is supported by the triangle front support 31 and a rear side of the stationary shaft 3 is supported by the blank rear shaft support 413 which extends outwardly . a center portion of the stationary shaft 3 mates with the ceramic bearing 79 for supporting the rotation of the inner rotor 7 , and the length of the center portion of the stationary shaft 3 satisfies the length of ceramic bearing 79 and reserves an axial free - movement space for the inner rotor 7 . the ring slot 413 b of the blank rear shaft support 413 is tightly combined with and supported by the monitoring shaft metal rear support 821 b of the motor rear casing 82 and provides a hold length l . moreover , the ring slot 413 b may overcome the problem of the reduced strength of plastic material due to the rising of the temperature . the canned motor 8 comprises the stator 83 , a motor casing 81 , the motor rear casing 82 and the inner rotor 7 . the stator 83 is tightly fixed in the motor casing 81 . windings 831 are winded on the stator 83 . a pwm electric power , applied on the windings 831 , generates a magnetic flux to interact with a magnetic field of the inner rotor 7 . the inner rotor 7 generates torque and rotates to drive the type i impeller 5 to output hydraulic power . the type i containment shell 41 prevents the windings 831 of the stator 83 from being corroded by the corrosive fluid . the pump side flange 811 of the motor casing 81 is used for tightly fixing with the shell flange part 411 and the pump casing 4 to prevent the leakage from the corrosive fluid . a back flange of the motor casing 81 is used for fixing the motor rear casing 82 to provide a complete structure supporting so that the monitoring shaft metal rear support 821 b of the motor rear casing 82 may provide supporting needed by the stationary shaft 3 . the motor rear casing 82 is fixed with the motor casing 81 so that the monitoring shaft metal rear support 821 b , on the motor rear casing 82 , may provide supporting needed by the stationary shaft 3 . an electric power wire of the windings 831 of the stator 83 is connected to a drive power via a lead port 822 . the inner rotor 7 is a ring - shaped structure comprising the main magnets 71 , the rotor yoke 72 , the secondary magnets 73 and the axially extended part 76 . the number of the secondary magnets 73 is the same as the main magnets 71 . the secondary magnets 73 are assembled at one end of the inner side of a rotor yoke 72 of the inner rotor 7 in the vicinity of the bottom side of the type i containment shell 41 as well as face oppositely away from the main magnets 71 . a ceramic bearing 79 is installed in a central hole of the inner rotor 7 . the hub plate 52 is used for combining with the axially extended part 76 of the inner rotor 7 so that the type i impeller 5 and the inner rotor 7 are integrated into one piece or embedded to be combined with each other into one piece . when the pump operates , fluid flows along an inlet streamline 6 and is pressurized after flowing through the type i impeller 5 , such as an impeller exit streamline 61 . the pressurized fluid is output by an outlet 45 and a portion of the fluid , such as a turn back streamline 62 , enters the inner space 415 of the type i containment shell 41 via a rear side of the type i impeller 5 . after that , the fluid flows to the gap between an outer side of the inner rotor 7 and the inner space 415 of the type i containment shell 41 , continuing through another gap between the stationary shaft 3 and the ceramic bearing 79 . then , the fluid flows through the hub aperture 54 , such as an end lubrication streamline 65 , to an inlet of the type i impeller 5 . the circulating flowing of the fluid is used for providing the lubrication for the ceramic bearing 79 and taking away the heat generated by the inner rotor 7 . please refer to fig1 e , which is a cross - sectional view of a double - sided - supported stationary shaft with a monitor device and a lengthened bearing of the canned pump according to the present invention . this embodiment discloses the canned pump with a lengthened ceramic bearing 79 for heavy duty operation . therefore , in the structure design of the pump , the length of the rotor yoke 72 may be lengthened properly to meet with the length of the ceramic bearing 79 . the canned pump including a singled - sided - supported cantilever composited stationary shaft and a monitor device shown as in fig1 b , 3 b , 4 b and 5 b reference to fig1 d , 3 b , 4 b and 5 b , fig1 d is a cross - sectional view of a single - sided - supported cantilever composited stationary shaft with a monitor device of the canned pump according to the present invention , fig3 b is a cross - sectional view of a containment shell of a cantilever stationary shaft of the canned pump according to the present invention , fig4 b shows an axial hold length l of a cantilever stationary shaft according to the present invention and fig5 b shows a inner rotor bearing multiple forces and moments thereof on a single - sided - supported cantilever stationary shaft according to the present invention . the canned pump comprises a metal casing 4 a , a type ii impeller 5 a , a type ii containment shell 41 a , a monitor device 9 , a composited stationary shaft 3 a and a canned motor 8 . the metal casing 4 a which includes an inlet 44 , an outlet 45 and a flow channel 47 is used for containing the type ii impeller 5 a . the metal casing 4 a is a metal wok structure by casting . a casing liner 4 b , made of anti - corrosive plastic , is covered on an inner side of the metal casing 4 a . a front thrust ring 46 , installed at the inlet 44 in an inner side of the metal casing 4 a , is used for mating with a thrust bearing 53 of the type ii impeller 5 a to form an axial thrust bearing . the type ii impeller 5 a is installed in the metal casing 4 a . a hub plate 52 is used for being combined with an axially extended part 76 of an inner rotor 7 so that the type ii impeller 5 a and the inner rotor 7 are integrated into one piece or embedded with each other into one piece . a hub balance hole 54 a is a through hole at the center of a curve hub plate 55 for making circulating fluid re - circulate , for example , an end lubrication streamline 65 . the inlet 44 of the metal casing 4 a and the inlet of the type ii impeller 5 a form a smooth and increasing - inner - diameter channel without any disturbance , and the shape of the curve hub plate 55 is smooth curve shape as well . therefore , it is favorable for reducing the flow speed of the fluid to make sure the pump has good npshr ability . the type ii containment shell 41 a is a cup - shaped structure which has a rear shaft seat 418 including an aperture on a bottom side of the type ii containment shell 41 a . a shell flange part 411 , on a front side of the type ii containment shell 41 a , is combined with the metal casing 4 a and a pump side flange 811 of the canned motor 8 , which prevents corrosive fluid from leakage . a shell column part 412 on a lateral side of the type ii containment shell 41 a , is passed through the inner side of the stator 83 with a loose slide fit . also , the bottom side of the type ii containment shell 41 a is tightly attached to the motor rear casing 82 a with sufficient supporting strength . the rear shaft seat 418 , on the center on the bottom side of the type ii containment shell 41 a , extends inwardly towards the inner side of a rotor yoke 72 . the rear shaft seat 418 further protrudes inwardly and includes an aperture 418 a installed at an inner side of the rear shaft seat 418 and a concave aperture 418 b installed on an outer side of the rear shaft seat 418 corresponding to each other . the aperture , installed on the center of the rear shaft seat 418 , is used for containing the composited stationary shaft 3 a . a seal surface 418 d of the rear shaft seat 418 is tightly attached by a surface of a ceramic shaft sleeve 33 including an o ring and a monitoring composited shaft metal rear support 821 d of the motor rear casing 82 a so that there is no leakage . the monitor device 9 , positioned on a ring - shaped surface of the concave aperture 418 b of the rear shaft seat 418 which extends axially , is used for detecting the wear of a bearing . the structure of the monitor device 9 comprises multiple secondary magnets 73 and a monitor set 93 . the number of the secondary magnets 73 is the same as the main magnets 71 . the secondary magnets 73 are assembled at one end of the inner side of a rotor yoke 72 of the inner rotor 7 in the vicinity of the bottom side of the type i i containment shell 41 a as well as face oppositely away from the main magnets 71 . the axial length of the secondary magnets 73 is at least more than twice as great as the length of an axial movement ( including the axial wear of the bearing ) of the inner rotor 7 . the monitor set 93 comprises the secondary yoke 91 and multiple signal coil pairs 92 . the secondary yoke 91 take the position at the center of the secondary magnets 73 as a reference point , the axial length of the secondary yoke 91 is divided into two sections , a front section and a rear section . when the secondary magnets 73 are moved , two axial ends of the secondary magnets 73 do not exceed the ranges of the two sections of the secondary yoke 91 . the composited stationary shaft 3 a , which is a cantilever supported structure , comprises a ceramic shaft sleeve 33 , a metal shaft 32 and a motor rear casing 82 a . the composited stationary shaft 3 a and the type ii containment shell 41 a form a completely sealed shaft system . when an end of the composited stationary shaft 3 a is installed on the monitoring composited shaft metal rear support 821 d of the motor rear casing 82 a , a required supporting strength is provided . the metal shaft 32 passes through a sleeve central hole 332 of the ceramic shaft sleeve 33 with the circular head 321 of the metal shaft 32 pressed tightly against the front end surface 333 of the ceramic shaft sleeve 33 . the teeth part 323 of the metal shaft 32 passes through to the rear shaft seat 418 and a central hole of the monitoring composited shaft metal rear support 821 d of the type ii containment shell 41 a which is extended inwardly in an axial direction . a nut of the teeth part 323 is fixed on the motor rear casing 82 a so that a surface of a sliding thrust surface 331 of the ceramic shaft sleeve 33 is tightly pressed against a surface of the monitoring composited shaft metal rear support 821 d . a circular head 321 of the metal shaft 32 is covered with a resin enclosure 322 , and an o ring is installed on the circular head 321 which is used for sealing and corrosion resistance . the sliding thrust surface 331 of the ceramic shaft sleeve 33 is used for mating with the ceramic bearing 79 of the inner rotor 7 to form an axial thrust bearing . a surface of the sliding thrust surface 331 and a surface of the monitoring composited shaft metal rear support 821 d of the motor rear casing 82 a are tightly fixed and compressed with each other , and a seal surface 418 d of the rear shaft seat 418 packed tightly between the sliding thrust surface 331 and the monitoring composited shaft metal rear support 821 d , and press an o ring to make sure there is no leakage , thereby forming a composited stationary shaft 3 a with high stiffness . the canned motor 8 comprises the stator 83 , a motor casing 81 , the motor rear casing 82 a and the inner rotor 7 . the stator 83 is tightly fixed in the motor casing 81 . windings 831 are winded on the stator 83 . a pwm electric power , applied on the windings 831 , may generate a magnetic flux to interact with a magnetic field of the inner rotor 7 , so the inner rotor 7 generates torque and rotates to drive the type ii impeller 5 a to output hydraulic power . the type ii containment shell 41 a prevents the windings 831 of the stator 83 from being corroded by the corrosive fluid . the pump side flange 811 which is fixed on a lateral pump side of the motor casing 81 and also fixing the shell flange part 411 and the metal casing 4 a for preventing the corrosive fluid from leakage . a back flange of the motor casing 81 is used for fixing with the motor rear casing 82 a to provide a complete structure supporting so that the monitoring composited shaft metal rear support 821 d of the motor rear casing 82 a may provide support which is required by the composited stationary shaft 3 a . the motor rear casing 82 a is tightly fixed with the back flange of the motor casing 81 so that the monitoring composited shaft metal rear support 821 d of the motor rear casing 82 a may provide support which is required by the composited stationary shaft 3 a . an electric power wire of the windings 831 of the stator 83 is connected to a drive power via a lead port 822 . the inner rotor 7 is a ring - shaped structure comprising the multiple main magnets 71 , a rotor yoke 72 , multiple secondary magnets 73 and the axially extended part 76 . the number of the secondary magnets 73 is the same as the main magnets 71 . the secondary magnets 73 are assembled at one end of the inner side of a rotor yoke 72 of the inner rotor 7 in the vicinity of the bottom side of the type i containment shell 41 as well as face oppositely away from the main magnets 71 . the secondary magnets 73 is covered by a ring - shaped rotor resin enclosure 74 which is made of an engineering plastic with anti - corrosion property . a ceramic bearing 79 is installed in a central hole of the inner rotor 7 . the hub plate 52 is used for combining with the axially extended part 76 of the inner rotor 7 so that the type ii impeller 5 a and the inner rotor 7 are integrated into one piece or embedded to be combined with each other into one piece . when the pump operates , fluid flows along an inlet streamline 6 and is pressurized after flowing through the type ii impeller 5 a , such as an impeller exit streamline 61 . the pressurized fluid is output by an outlet 45 , and a portion of the fluid , such as a turn back streamline 62 , enters the inner space 415 of the type ii containment shell 41 a via a rear side of the type ii impeller 5 a in the mean time . after that , the fluid flows to the gap between an outer side of the inner rotor 7 and the inner space 415 of the type ii containment shell 41 a , continuing through another gap between of the composited stationary shaft 3 a and the ceramic bearing 79 . then , the fluid flows through a hub balance hole 54 a which is at the center of the curve hub plate 55 , such as an end lubrication streamline 65 , to an inlet of the type ii impeller 5 a . the circulating flowing of the fluid is used for providing the lubrication for the ceramic bearing 79 and taking away the heat generated by the inner rotor 7 . please refer to fig2 , which is a cross - sectional view of an inner rotor 7 of a motor and a type i impeller 5 integrated into one unit according to the third embodiment . the structure in this embodiment is also applicable to other embodiments in this invention . the ceramic bearing 79 , installed in a hollow part of the inner rotor 7 , is used for mating with the stationary shaft 3 to form a hydrodynamic bearing which is used for supporting the rotation of the inner rotor 7 and transmitting the motor power . the axially extended part 76 is used for being combined with the hub plate 52 to transmit the torque of the inner rotor 7 . the secondary magnets 73 are assembled at one end of the inner side of a rotor yoke 72 of the inner rotor 7 as well as face oppositely away from the main magnets 71 . the secondary magnets 73 and the inner rotor 7 are encapsulated together for preventing corrosion . the number of the secondary magnets 73 is the same as the main magnets 71 but the size of the secondary magnets 73 is less than one tenth of the main magnets 71 . please refer to fig3 a , which is a cross - sectional view of a containment shell of a double - sided - supported stationary shaft of the canned pump according to the present invention . take the type i containment shell 41 in the third embodiment for an example , the assembly of the ring slot 413 b and the monitor set 93 are described as followed . the type i containment shell 41 is a cup - shaped structure without any through hole so that there is no leakage . the blank rear shaft support 413 at the center of the bottom side of the type i containment shell 41 extends inwardly . the axially extended length g is extended from the bottom side of the type i containment shell 41 towards the shell flange part 411 . the blank rear shaft support 413 protrudes from the inner side and has the central shaft hold hole 413 a whose depth h is from the opening of the blank rear shaft support 413 to the bottom side of the shaft hold hole 413 a . the ring slot 413 b is on the outer side of the type i containment shell 41 . the rear thrust ring 414 is on the front surface of the shaft hold hole 413 a . the monitor set 93 , including the secondary yoke 91 and the signal coil pairs 92 , may be positioned on the ring slot 413 b which is on the outer side of the blank rear shaft support 413 . the type i containment shell 41 is only used for providing anti - corrosion isolating ability without providing stiff supporting for the stationary shaft 3 please refer to fig3 b , which is a cross - sectional view of a containment shell of a cantilever stationary shaft of the canned pump according to the present invention . take the type ii containment shell 41 a of the fourth embodiment as an example . the assembly of the concave aperture 418 b and the monitor set 93 are described as followed . the type ii containment shell 41 a is a cup - shaped shell structure comprising a hole which is on the center of the bottom side and is used for containing the composited stationary shaft 3 a ( shown in fig1 c ). the rear shaft seat 418 on the center on the bottom side of the type ii containment shell 41 a , extends inwardly in the inner space . the rear shaft seat 418 is a convex structure having an aperture 418 a and protruding from the inner side . the axially extended length g extends from the bottom side of the type ii containment shell 41 a towards the shell flange part 411 to the seal surface 418 d . the outer side of the rear shaft seat 418 corresponds to the concave aperture 418 b . the monitor set 93 positioned on an inner ring - shaped surface of the concave aperture 418 b , includes the secondary yoke 91 and the multiple signal coil pairs 92 . the secondary yoke 91 is tightly attached to the monitoring composited shaft metal rear support 821 d . the composited stationary shaft 3 a ( shown in fig1 c ) is installed in the aperture which is at the center of the rear shaft seat 418 . the seal surface 418 d of the rear shaft seat 418 is tightly pressed by the surface of the surface of the sliding thrust surface 331 of the ceramic shaft sleeve 33 ( shown in fig1 c ) including the o ring and the monitoring composited shaft metal rear support 821 d of the motor rear casing 82 a , which makes sure that there is no leakage from the type ii containment shell 41 a . the stiffness support of the composited stationary shaft 3 a is completely comes from the motor rear casing 82 a and the hold length l of the monitoring composited shaft metal rear support 821 d . please refer to fig4 a , which shows an axial hold length l of a double - sided - supported stationary shaft according to the present invention . take the double - sided supported stationary shaft 3 as an example . the axial hold length l is described as followed . the blank rear shaft support 413 is positioned at the center of the bottom side of the type i containment shell 41 and extends inwardly and axially to an inner space of the rotor yoke 72 ( shown in fig1 a ). the blank rear shaft support 413 includes the shaft hold hole 413 a ( shown in fig3 a ) protruding inwardly and positioned in the blank rear shaft support 413 , and the ring slot 413 b ( shown in fig3 a ) positioned on the outer side of the blank rear shaft support 413 . the monitor set 93 , which includes the secondary yoke 91 and the signal coil pairs 92 , is installed in the ring slot 413 b ( shown in fig3 a ). the strength of the shaft hold hole 413 a ( shown in fig3 a ), which is supported by the monitoring shaft metal rear support 821 b of the motor rear casing 82 and the secondary yoke 91 tightly combined to each other , is provided by the outer sidewall of the haft hold hole 413 a the bottom side of the shaft hold hole 413 a is completely fitted with the inner side of the backward bulged part 823 of the motor rear casing 82 . the length of the bulged part 823 is fitted with the hold length l of the shaft hold hole 413 a for providing the high - stiff support . that is , the type i containment shell 41 is only used for providing anti - corrosion isolating ability without providing stiff support for the stationary shaft 3 . the hold length l is determined by the axially extended length g of the blank rear shaft support 413 and the hold hole depth h so that the axial stiff support may be practically provided . the longer the hold length l is , the much the problem of reduced plastic strength because of the rise of the temperature is solved . please refer to fig4 b , which shows an axial hold length l of a cantilever stationary shaft according to the present invention . take the hold length l of the cantilever composited stationary shaft 3 a ( shown in fig1 c ) as an example which is described as followed . the type ii containment shell 41 a which is the cup - shaped shell structure includes the rear shaft seat 418 positioned at the center of the bottom side , extending inwardly and axially in the inner space of the rotor yoke 72 , and for containing the composited stationary shaft 3 a ( shown in fig1 c ). the rear shaft seat 418 is a convex structure having an aperture 418 a and protruding from the inner side and is a concave aperture 418 b at the outer side . the monitor set 93 is installed on the inner ring - shaped surface of the concave aperture 418 b . the seal surface 418 d of the rear shaft seat 418 is tightly pressed by the surface of the surface of the sliding thrust surface 331 of the ceramic shaft sleeve 33 ( shown in fig1 c ) including the o ring and the monitoring composited shaft metal rear support 821 d of the motor rear casing 82 a the longer the hold length l is , the greater the force and the moment can be borne . the composited stationary shaft 3 a structure according to the invention may avoid the problem that the strength of the plastic material of the type ii containment shell 41 a may be reduced due to the rise of the temperature . please refer to fig5 a , which shows an inner rotor bearing multiple forces and moments thereof on a double - sided - supported stationary shaft according to the present invention . take the inner rotor 7 which bears the multiple forces and moments thereof on the double - sided supported stationary shaft 3 according to the first and the third embodiments as an example which is described as followed . the stationary shaft 3 is made of anti - corrosion and anti - wear ceramic material . the front end of the stationary shaft 3 is supported by the plastic triangle front support 31 , and the rear end of the stationary shaft 3 is supported and fixed by the blank rear shaft support 413 extending axially . the strength of the blank rear shaft support 413 is provided by the monitoring shaft metal rear support 821 b and the secondary yoke 91 which are tightly combined with each other . the center portion of the stationary shaft 3 mates with the ceramic bearing 79 , which is used for supporting the rotation of the inner rotor 7 . the length of the center portion satisfies with the length of the ceramic bearing 79 and reserves the axial free - movement space of the inner rotor 7 . such as a , b , c in the figure , when the inner rotor 7 actually rotates , a rear axial free space a exists between the ceramic bearing 79 and the rear thrust ring 414 , a front axial free space c exists between the ceramic bearing 79 and the triangle front support 31 , and an axial gap b exists between the inner rotor 7 and the type i containment shell 41 . the above - mentioned gaps ( spaces ) may be varied due to the wear of surfaces of the front thrust ring 46 , the thrust bearing 53 , the rear thrust ring 414 and the ceramic bearing 79 . in most cases , the inner rotor 7 is moved forward because of the axial thrust by the type i impeller 5 to make the front thrust ring 46 mate with the thrust bearing 53 to slidably rotate . thus , the axial width of the front axial free space c must be greater than the sum of the amount of wear allowance of the front thrust ring 46 and the thrust bearing 53 , and the width of the axial gap b is increased accordingly when the front axial free space c is reduced . however , when the pump rotates in the condition of high flow rate and low head , the inner rotor 7 may be moved backward because of the axial momentum of the fluid to make the rear thrust ring 414 mate with ceramic bearing 79 to slidably rotate and the width of the rear axial free space a is reduced to zero . therefore , the width of the axial gap b must be greater than the total amount of the rear axial free space a , and the wear of the surface of the ceramic bearing 79 and the surface of the rear thrust ring , which prevents the inner rotor 7 from contacting the type i containment shell 41 directly , thereby resulting in the damage . in other words the axial free - movement distance of the inner rotor 7 is equaled to the sum of the rear axial free space a and the front axial free space c , and because the amount of size deformation of the plastic type i containment shell 41 and the pump casing 4 is usually big , the reserved gap size must include manufacturing tolerance . under the above - mentioned operation conditions , the stationary shaft 3 and the supporting structure thereof must bear the multiple loading including an inner rotor weight w , an eccentric centrifugal force x , a radial force p and moments of these forces . the inner rotor weight w is the force generated by the weight of the inner rotor 7 . the eccentric centrifugal force x is generated by the centroid of the inner rotor 7 resulted from the gaps of the ceramic bearing 79 . the radial force p , generated from the uneven fluid pressure of the flow channel 47 of the pump casing 4 , applies on the outlet surface of the type i impeller 5 . the weight moment is equaled to the inner rotor weight w multiplied by a weight arm length wl . the centrifugal moment is equaled to the eccentric centrifugal force x multiplied by an eccentric length xl . the moment of radial force is equaled to the radial force p multiplied by a radial force arm length pl . those forces and moments apply on the stationary shaft 3 . the strength of the triangle front support 31 made of anti - corrosive plastic material is reduced when the temperature rises , and therefore most of the forces and the moments are borne by the supporting structure on the rear end of the stationary shaft 3 . the eccentric centrifugal force x varying with the wearing of the ceramic bearing 79 is the most main variable loading applied on the stationary shaft 3 . the greater the amount of the wear is , the greater the eccentric centrifugal force x is . the second main variable loading applied on the stationary shaft 3 is the radial force p from the uneven fluid pressure of the outlet surface of the impeller 5 . the longest radial force arm length is from the outer diameter of the impeller 5 to the rear end of the stationary shaft 3 , which causes the skew between the center of the inner rotor 7 and the axis of the stationary shaft 3 , thereby making the supporting structure deformed continuously . because the axially extended length g substantially reduces the length of the radial force arm length , and the hold length l increases the moment bearing ability of the stationary shaft 3 . the above - mentioned skew and structure deformation problem may be alleviated and improved , and therefore , the requirement for the strength of the supporting structure of the triangle front support 31 positioned at the front end of the stationary shaft 3 may be greatly reduced . please refer to fig5 b , which is an inner rotor bearing multiple forces and moments thereof on a single - sided - supported cantilever stationary shaft according to the present invention . take the inner rotor 7 bearing the multiple forces and moments thereof on the single - sided supported composited stationary shaft 3 a according to the second and the fourth embodiments as an example which is described as followed . the composited stationary shaft 3 a is made of the metal shaft 32 and the ceramic shaft sleeve 33 . when the end of the composited stationary shaft 3 a is installed on the monitoring composited shaft metal rear support 821 d of the motor rear casing 82 , the needed supporting strength may be obtained . the metal shaft 32 passes through the sleeve central hole 332 of the ceramic shaft sleeve 33 , and the end of the circular head 321 is tightly pressed against the front end surface 333 of the ceramic shaft sleeve 33 . the teeth part 323 of the metal shaft 32 passes through the rear shaft seat 418 of the type ii containment shell 41 a and the central hole of the monitoring composited shaft metal rear support 821 d , and is fixed with the motor rear casing 82 by the metal shaft 32 . the surface of the sliding thrust surface 331 of the ceramic shaft sleeve 33 may be tightly pressed against the surface of the monitoring composited shaft metal rear support 821 d so that the composited stationary shaft 3 a with high stiffness is formed . the composited stationary shaft 3 a , whose length satisfies the length requirement for the ceramic bearing 79 , mates with ceramic bearing 79 for supporting the rotation of the inner rotor 7 , and reserves the axial free - movement space of the inner rotor 7 , such as a , b . when the inner rotor 7 actually operates , a rear axial free space a exists between the ceramic bearing 79 and the rear thrust ring 414 , an axial gap b exists between the inner rotor 7 and the type ii containment shell 41 a . the two above - mentioned gaps are varied because of the wearing of the front thrust ring 46 , the thrust bearing 53 , the rear thrust ring 414 and the ceramic bearing 79 . under most conditions , the inner rotor 7 is moved forward by the axial thrust of the type ii impeller 5 a so that the front thrust ring 46 mates with the thrust bearing 53 to slidably rotate . the width of the axial gap b is increased accordingly . when the pump operates in the condition of high flow rate and low head , the inner rotor 7 is moved backward because of the axial momentum of the fluid , which makes the rear thrust ring 414 mate with the ceramic bearing 79 to slidably rotate and the width of the rear axial free space a is reduced to zero . therefore , the width of the axial gap b must be greater than the sum of the rear axial free space a and the amount of wear of the surface of the ceramic bearing 79 and the rear thrust ring 414 , which prevents the inner rotor 7 from directly contacting the type ii containment shell 41 a , thereby causing the damage . in other words , the rear axial free space a is varied according to the axial free - movement of the inner rotor 7 , because the amount of size deformation of the plastic type ii containment shell 41 a is usually big , each of the reserved gap sizes must include manufacturing tolerance . under the above - mentioned operation conditions , the composited stationary shaft 3 a and the supporting structure thereof must bear the multiple loading including an inner rotor weight w , an eccentric centrifugal force x , a radial force p and moments of these forces . the inner rotor weight w is the force generated by the weight of the inner rotor 7 . the eccentric centrifugal force x is generated by the centroid of the inner rotor 7 resulted from the gaps of the ceramic bearing 79 . the radial force p , generated from the uneven fluid pressure of the flow channel 47 of the metal casing 4 a , applies on the outlet surface of the type ii impeller 5 a . the weight moment is equaled to the inner rotor weight w multiplied by a weight arm length wl . the centrifugal moment is equaled to the eccentric centrifugal force x multiplied by an eccentric length xl . the moment of the radial force is equaled to the radial force p multiplied by a radial force arm length pl . those forces and moments apply on the composited stationary shaft 3 a , and are borne by the metal composited support . the eccentric centrifugal force x varying with the wearing of the ceramic bearing 79 is the most main variable loading applied on the composited stationary shaft 3 a . the greater the amount of the wear is , the greater the eccentric centrifugal force x is . the second main variable loading applied on the composited stationary shaft 3 a is the radial force p from the uneven fluid pressure of the outlet surface of the impeller 5 . the longest radial force arm length is from the outer diameter of the impeller 5 to the rear end of the composited stationary shaft 3 a , which causes the skew between the center of the inner rotor 7 and the axis of the composited stationary shaft 3 a , thereby making the supporting structure deformed continuously . because the axially extended length g substantially reduces the length of the radial force arm length and the hold length l increases the moment bearing ability of the composited stationary shaft 3 a , the above - mentioned skew and structure deformation problem may be alleviated and improved . a monitor device of the canned pump for detecting the wear of a bearing , fig6 a , 6 b , 6 c , 6 d please refer to fig6 a , which is a radial cross - sectional view of a monitor device for detecting the wear of a bearing of a motor according to the present invention . the figure takes an eight - poles - and - eight - coils design for an example , but is not limited to the invention . other designs or methods may achieve the same effect according other embodiments . a monitor device 9 comprises multiple secondary magnets 73 and a monitor set 93 .□ the secondary magnets 73 are assembled at one end of the inner side of a rotor yoke 72 of the inner rotor 7 in the vicinity of the bottom side of the type i containment shell 41 as well as face oppositely away from the main magnets 71 . the number of the secondary magnets 73 is the same as the main magnets 71 but the size of the secondary magnets 73 is less than one tenth of the main magnets 71 , and the area and the thickness of the secondary magnets 73 at least provide the magnetomotive force ( mmf ) and the magnetic flux which are needed by the signal coil pairs . here , the circumference of the inner rotor 7 is divided into eight pieces according to the number of the secondary magnets 73 and each of them has an electric included angle of 180 degrees and a space included angle of 45 degrees . the main magnetic flux lines emits from a surface of a forward flux magnet 71 a and passes through a motor magnetic gap 98 to a stator teeth 83 a of a stator 83 , continues to the adjacent stator teeth 83 c via a stator yoke 83 b , and passes through the motor magnetic gap 98 again , then to a original adjacent backward flux magnet 71 b , and returns back to the original forward flux magnet 71 a via the rotor yoke 72 so that the stator yoke magnetic route 96 a is formed ( hereafter called main magnetic loop ) the secondary magnetic flux lines emit from a surface of the forward flux secondary magnet 73 a to the secondary yoke 91 through the monitoring magnetic gap 97 , and via a secondary yoke 92 pass through the monitoring magnetic gap 97 again , and back to an original adjacent backward flux secondary magnet 73 b and another backward flux secondary magnet 73 c , respectively , and return back to the original secondary magnets 73 a through the rotor yoke 72 so that the rotor yoke magnetic route 96 is formed ( hereafter called secondary magnetic loop ), and the secondary magnetic loop passes through the monitor device therefore , the main magnetic loop and the secondary magnetic loop coexist in the rotor yoke 72 . that is , the magnetic flux lines of the monitor device 9 pass through the rotor yoke 72 without being disturbed . when the inner rotor 7 rotates , the monitor device 9 outputs an electromotive force signal ( i . e . a voltage signal ) by cutting the secondary magnetic flux lines so the voltage signal is independent and the interference of an outer voltage is avoided . the monitor set 93 comprises the secondary yoke 91 and the multiple signal coil pairs 92 . the multiple signal coil pairs 92 , installed on a surface of the secondary yoke 91 , comprises front signal coil pairs 92 a and rear coil pairs 92 b which are axially and tightly arranged side by side and are aligned with a secondary magnet center 73 g ( shown in fig6 c ). moreover , the signal coil pairs 92 are divided into two groups of coils , signal coils α and signal coils β , along a circumferential direction . each of the groups has two signal coil pairs , which are corresponding to each other in a radial direction of 180 degrees . eight signal coils , which include a signal coil α 11 , a signal coil α 12 , a signal coil α 21 , a signal coil β 22 , a signal coil β 11 , a signal coil β 12 , a signal coil β 21 , a signal coil β 22 , have the same size , and the difference between the electric included angle of the signal coils α and the signal coils β is 90 degrees ( or 270 degrees ) and the difference between the space included angle θ of the signal coils α and the signal coils β is 112 . 5 degrees ( or 67 . 5 degrees ). the front signal coil pairs 92 a comprise a signal coil α 11 , a signal coil α 21 , a signal coil β 11 and a signal coil β 21 . the rear signal coil pairs 92 b comprise a signal coil α 12 , a signal coil α 22 , a signal coil β 12 and a signal coil β 22 . the positioning of the electric included angles and the space included angles of the above - mentioned signal coil pairs 92 are obtained by a magnet alignment point 911 ( shown in fig6 c ) of a secondary yoke rear end 91 b of the secondary yoke 91 . the magnet alignment point 911 aligns with the center of the signal coils α 11 , and when the electric included angle of the magnet alignment point 911 is 90 degrees and the space included angle of the magnet alignment point 911 is 22 . 5 degrees , it is favorable for repairing and exchanging the monitor set 93 . the length of the ring - shape secondary yoke 91 of the independent monitor device 9 is longer than the sum of the axial length of the rotor yoke 72 and the axial movement length of the inner rotor 7 , and is longer than the total axial length of the signal coil pairs 92 ( including the limit value of the wear of thrust bearing ). the width of the circumference of the signal coil pairs 92 is not greater than the electric included angle of 180 degrees . the secondary yoke front end 91 a and the secondary yoke rear end 91 b completely cover the signal coil pairs 92 , which makes sure that when the inner rotor 7 is moved axially , the magnetic flux lines of the rotor yoke magnetic route 96 of the secondary magnets still can be stable as well as prevent the deformation and the bending , thereby ensuring the stability and the linearity of the voltage signal of the signal coil pairs 92 . when the inner rotor 7 is moved both in a radial and an axial direction , the differential voltage signals of the signal coil pairs 92 are obtained . the differential voltage signals of different combinations of the signal coil pairs may represent an axial movement or a radial movement . when the amount of movement exceeds the axial free space or a gap of the ceramic bearing 79 , it shows that the wear of the bearing happens and the amount of the wears can be calculated . when the movement exceeds a wear warning value , a warning notice must be transmitted , and when the movement exceeds a wear limit value , the operation of the pump must be stopped . please refer to fig6 b , 6 c and 6 d . fig6 b is an axial cross - sectional view of a monitor device for detecting the wear of a bearing according to the present invention ; fig6 c is a schematic view of a monitor device for detecting the wear of a bearing utilizing eight signal coil pairs according to the present invention ; and fig6 d is a schematic perspective view of a monitor device for detecting the wear of a bearing according to the present invention . the figures show an actual way of arranging signal coil pairs of a monitor device for detecting the wear of a bearing and a method for calculating the voltage signals . the figures take an eight - poles - and - eight - coils design for an example , but not limited to the invention . other designs and calculating methods may achieve the same effect according other embodiments . the monitor device 9 comprises eight signal coil pairs 92 , which include a signal coil α 11 , a signal coil α 12 , a signal coil α 21 , a signal coil α 22 , a signal coil β 11 , a signal coil β 12 , a signal coil β 21 , a signal coil β 22 . when the inner rotor 7 rotates , a rotating magnetic field is formed between the secondary magnets 73 and the signal coil pairs 92 and the voltage signals is outputted , and this voltage signals can be calculated by a d - q axis transform method and is converted into an axial and a radial movements of the inner rotor 7 which can be the criterion of the wear of the bearing . the corresponding specification is described hereinafter : signals of the eight signal coil pairs of the monitor device 9 take an average value as the signal values , which are : because the above - mentioned average value signals are not affected by the axial wear and the radial wear of the bearing ; and the electric included angle difference between the signals of e αt and e βt is 90 degrees . suppose the equations of e αt and e βt are : e αt = λ mt ′ ω r cos θ r − ƒ ( 2 ) e βt = λ mt ′ ω r sin θ r − ƒ ( 3 ) in the above - mentioned equations , ω r is the rotation speed , λ mt is a flux linkage between the secondary magnets 73 and the signal coil pairs 92 , θ r − ƒ is the relative angular positions of the secondary magnets between α and β signal coils of the monitor device 9 . ω r and θ r − ƒ from the above - mentioned equations ( 2 ) and ( 3 ) can be calculated as : wherein λ mt ′ can be obtained by measuring . the mechanical rotation speed and the relative mechanical angular position can be obtained by the following equations : in order to calculate the axial wear and the radial wear of the bearing , each signal of the signal coil pairs 92 is put into transformation matrixes to convert signals into d - q axes coordinates , shown as followed : the greater of the following two difference values is taken as the criteria of the axial movement and the wear of the bearing : the greater of the following two difference values is taken as the criteria of the radial movement and the wear of the bearing : the greater of the following two difference values is taken as the total criteria of the radial movement , the axial movement and the wear of the bearing : the value of the eccentric movement and the angular position of the inner rotor 7 , that is , the actual movement track of the inertial center of the inner rotor , can be calculated according to the above - mentioned equations . a monitor device for detecting the wear of a bearing of the canned pump , fig6 e please refer to fig6 e , which is a schematic view of a monitor device for detecting the wear of a bearing utilizing two pairs of signal coils according to the present invention . compared to the fifth embodiment , the number of signal coil pairs 92 of monitor device 9 for detecting the wear of a bearing is reduced to four according to this embodiment . the figure takes an eight - poles - and - four - coils design for an example , but is not limited to the invention . other designs or methods may achieve the same effect according other embodiments . the area and the thickness of secondary magnets 73 at least provide the magnetomotive force ( mmf ) and the magnetic flux which are needed by the signal coil pairs . a monitor set 93 comprises a secondary yoke 91 and the multiple signal coil pairs 92 . here , the circumference of an inner rotor 7 is divided into eight pieces according to the number of the secondary magnets 73 and each of them has an electric included angle of 180 degrees and a space included angle of 45 degrees . the signal coil pairs 92 are divided into two groups including signal coils α and signal coils β . the signal coils α comprise a signal coil α 1 and a signal coil α 2 , and the signal coils β comprise a signal coil β 1 and a signal coil β 2 . the differences of electric included angle and the space included angle between the signal coils α and β are 90 degrees ( or 270 degrees ) and 112 . 5 degrees ( or 67 . 5 degrees ), respectively . each of the groups has two signal coil pairs , which are corresponding to each other in a radial direction of 180 degrees . the signal coils α 1 , α 2 , β 1 and β 2 have the same size and the axial length of each of the coils α 1 , α 2 , β 1 and β 2 is not less than the sum of the length of the secondary magnets 73 and the length of the axial free - movement of the inner rotor 7 ( including the limit value of the wear of thrust bearings ), and the width of the circumference of each signal coils is not greater than the electric included angle of 180 degrees . front ends of each of the signal coils α 1 and β 2 align with a secondary yoke front end 91 a of the secondary yoke 91 . rear ends of each of the signal coils α 1 and β 2 align with a secondary magnet rear end 73 f of the secondary magnets 73 . front ends of each of the signal coils α 2 and β 1 align with a secondary magnet front end 73 e of the secondary magnets 73 . rear ends of each of the signal coils α 2 and β 1 align with a secondary yoke rear end 91 b of the secondary yoke 91 . in other words , the signal coils α 1 , α 2 , β 1 and β 2 are axially arranged in a stagger way and axially aligned with the front and the rear ends of the secondary magnets 73 . the positions of the electric angle and the space angle of the above - mentioned signal coil pairs 92 are obtained by a magnet alignment point 911 which is positioned on the secondary yoke rear end 91 b of the secondary yoke 91 and corresponds to the center of the signal coils α 1 . the electric angle and the space angle of the magnet alignment point 911 are 90 degrees and 22 . 5 degrees , respectively so that it is favorable for repairing and exchanging the monitor set 93 conveniently . the axial length of the secondary yoke 91 is greater than the total axial length of the arranged signal coil pairs 92 and the secondary yoke front end 91 a and the secondary yoke rear end 91 b may completely cover the signal coil pairs 92 for ensuring that when the inner rotor 7 is moved axially , the magnetic flux lines of the secondary magnetic loop of the secondary magnets 73 may be stable without deformation or bending , maintaining itself to be distributed on the surface of the secondary yoke 91 stably , thereby ensuring the stability and linearity of a voltage signal of the signal coil pairs 92 . the axial movement and the radial movement of the inner rotor 7 can be calculated from the difference value of these voltage signals of the signal coil pairs 92 . when the amount of movement exceeds the axial free space or a gap of the ceramic bearing 79 , it shows that the wear of the bearing happens and the amount of the wears can be calculated . when the movement exceeds a wear warning value , a warning notice must be transmitted , and when the movement exceeds a wear limit value , the operation of the pump must be stopped . signals of the four signal coils of the monitor device 9 take an average value as the signal values , which are : because the above - mentioned average value signals are not affected by the axial wear and the radial wear of the bearing ; and the electric included angle difference between the signals of e αt and e βt is 90 degrees . suppose the equations of e αt and e βt are : e αt = λ mt ′ ω r cos θ r − ƒ ( 14 ) e βt = λ mt ′ ω r sin θ r − ƒ ( 15 ) in the above - mentioned equations , ω r is the rotation speed , λ mt is a flux linkage between the secondary magnets 73 and the signal coil pairs 92 , θ r − ƒ is the relative angular positions of the secondary magnets between α and β signal coils of the monitor device 9 . ω r and θ r − ƒ from the above - mentioned equations ( 14 ) and ( 15 ) can be calculated as : wherein λ mt ′ can be obtained by measuring . the mechanical rotation speed and the relative mechanical angular position can be obtained by the following equations : in order to calculate the axial wear and the radial wear of the bearing , each signal of the signal coil pairs 92 is put into transformation matrixes to convert signals into d - q axes coordinates , shown as followed : the following difference value is taken as the criteria of the axial movement and the wear of the bearing : the following difference value is taken as the criteria of the radial movement and the wear of the bearing : the total criteria of the radial movement , the axial movement and the wear of the bearing may consider ε a and ε r . the value of the eccentric movement and the angular position of the inner rotor 7 , that is , the actual movement track of the inertial center of the inner rotor , can be calculated according to the above - mentioned equations . please refer to fig7 , which is a schematic view of a monitor device of the canned pump including a hall sensor according to the present invention . the figure takes a composited monitor device 9 including three hall sensors 94 with eight poles and four signal coils as an example , but is not limited to the invention . other designs may achieve the same effect . the signal coils are divided into two groups which are signal coils α and signal coils β . the signal coils α comprises a signal coil α 1 and a signal coil α 2 , and the signal coils β comprises a signal coil β 1 and a signal coil β 2 . the electric included angle between α and β signal coils is 90 degrees ( 270 degrees ) and the space included angle θ between α and β signal coils is 112 . 5 degrees ( 67 . 5 degrees ). the signal coils α 1 , α 2 , β 1 and β 2 have the same size and the axial length of each of the coils α 1 , α 2 , β 1 and β 2 is not less than the sum of the length of the secondary magnets 73 and the length of the axial free - movement of the inner rotor 7 ( including the limit value of the wear of thrust bearings ), and the width of the circumference of each signal coils is not greater than the electric included angle of 180 degrees . front ends of each of the signal coils α 1 and β 2 align with a secondary yoke front end 91 a of the secondary yoke 91 . front ends of each of the signal coils α 1 and β 2 align with a secondary yoke front end 91 a of the secondary yoke 91 . rear ends of each of the signal coils α 1 and β 2 align with a secondary magnet rear end 73 f of the secondary magnets 73 . front ends of each of the signal coils α 2 and β 1 align with a secondary magnet front end 73 e of the secondary magnets 73 . rear ends of each of the signal coils α 2 and β 1 align with a secondary yoke rear end 91 b of the secondary yoke 91 . in other words , the signal coils α 1 , α 2 , β 1 and β 2 are axially arranged in a stagger way and axially aligned with the front and the rear ends of the secondary magnets 73 . the positions of the electric angle and the space angle of the above - mentioned signal coil pairs 92 are obtained by a magnet alignment point 911 which is positioned on the secondary yoke rear end 91 b of the secondary yoke 91 and corresponds to the center of the signal coils α 1 . the electric angle and the space angle of the magnet alignment point 911 are 90 degrees and 22 . 5 degrees , respectively so that it is favorable for repairing and exchanging the monitor set 93 conveniently . the differences of the electric included angles and the space included angles between the three hall sensors 94 are 120 degrees and 30 degrees , respectively . the hall sensor 94 , at the center position among the three , is installed at the inner center of the signal coils α 2 , and the electric included angle and the space included angle of the center hall sensor 94 are 90 degrees and 202 . 5 degrees , respectively . the other two hall sensors 94 , whose the difference of the electric included angle is 120 degrees , is installed at two opposite side of an exterior surface of the signal coils α 2 , respectively . the axial length of the secondary yoke 91 is greater than the total axial length of the arranged signal coil pairs 92 and the secondary yoke front end 91 a and the secondary yoke rear end 91 b may completely cover the signal coil pairs 92 for ensuring that when the inner rotor 7 is moved axially , the magnetic flux lines of the secondary magnetic loop of the secondary magnets 73 may be stable without deformation or bending , maintaining itself to be distributed on the surface of the secondary yoke 91 stably , thereby ensuring the stability and linearity of a voltage signal of the signal coil pairs 92 . the axial movement and the radial movement of the inner rotor 7 can be calculated from the difference value of these voltage signals of the signal coil pairs 92 . when the amount of movement exceeds the axial free space or a gap of the ceramic bearing 79 , it shows that the wear of the bearing happens and the amount of the wears can be calculated . when the movement exceeds a wear warning value , a warning notice must be transmitted , and when the movement exceeds a wear limit value , the operation of the pump must be stopped . the method for calculating the wear of the bearing is the same as the sixth embodiment . when the inner rotor 7 rotates and the axial movement happens , the magnetic flux lines of the secondary magnetic loop is stable without deformation or bending for ensuring the stability of voltage signal of the hall sensors 94 so that a drive including the monitor sensor 9 for driving the canned pump is provided . the foregoing description of the exemplary embodiments of the invention has been presented only for the purposes of illustration and description and is not intended to be exhaustive or to limit the invention to the precise forms disclosed . many modifications and variations are possible in light of the above teaching . the embodiments were chosen and described in order to explain the principles of the invention and their practical application so as to activate others skilled in the art to utilize the invention and various embodiments and with various modifications as are suited to the particular use contemplated . alternative embodiments will become apparent to those skilled in the art to which the present invention pertains without departing from its spirit and scope . accordingly , the scope of the present invention is defined by the appended claims rather than the foregoing description and the exemplary embodiments described therein .