EP4102076A1 - Pumpengehäuse - Google Patents

Pumpengehäuse Download PDF

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Publication number
EP4102076A1
EP4102076A1 EP22177040.7A EP22177040A EP4102076A1 EP 4102076 A1 EP4102076 A1 EP 4102076A1 EP 22177040 A EP22177040 A EP 22177040A EP 4102076 A1 EP4102076 A1 EP 4102076A1
Authority
EP
European Patent Office
Prior art keywords
passage portion
pump
pump casing
discharge passage
discharge
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22177040.7A
Other languages
English (en)
French (fr)
Inventor
Soichiro Ogawa
Toshiyuki Nomura
Tsuyoshi USUI
Yoichi Nakamura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ebara Corp
Original Assignee
Ebara Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ebara Corp filed Critical Ebara Corp
Publication of EP4102076A1 publication Critical patent/EP4102076A1/de
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • F04D13/14—Combinations of two or more pumps the pumps being all of centrifugal type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • F04D15/029—Stopping of pumps, or operating valves, on occurrence of unwanted conditions for pumps operating in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

  • the present invention relates to a pump casing.
  • a pump apparatus is conventionally used for various applications in various kinds of houses and in a site such as a factory.
  • an inline pump in which a pump section and a motor section are integrated, and a suction port and a discharge port of a pump are arranged on the same line is widely used because the inline pump is easily attachable in a middle of a pipe.
  • the inline pump is installed in a construction facility, it is desirable to avoid stoppage of liquid supply when one inline pump has failed or one inline pump is subjected to periodic inspection.
  • twin pump in which two inline pumps are arranged in parallel, one suction port and one discharge port are connected to the two inline pumps, and the two inline pumps share one suction port and one discharge port. Note that, in the following, in a case where the two inline pumps do not share one suction port and one discharge port, namely, in a case where each of the two inline pumps includes one suction port and one discharge port, each of the pumps is called a single pump.
  • twin pump In the case where the twin pump is installed, if trouble occurs on one of the pumps, or the like, parts other than a casing of the pump having the trouble are detached, and an upper part of the casing is covered with a blank flange.
  • the parts other than the casing include an electric motor disposed on the upper part of the casing, a rotary shaft coupled to the electric motor, and an impeller fixed to the rotary shaft and housed in the casing.
  • operation can be continued by the other pump during a pump maintenance period or during a period when a spare part for the failed pump is prepared.
  • a pump manufacturer requires downsizing of devices to be incorporated in an own product in order to downsize the own product as much as possible.
  • a length of a header pipe to branch a pipe into pipes for two single pumps or to merge pipes can be reduced as compared with a case where the two single pumps are arranged in parallel.
  • a valve such as a check valve for backflow prevention is shared by the two pumps configuring the twin pump, which makes it possible to achieve space saving.
  • the twin pump manufacturer can meet space saving required by a customer. Further, alternately operating the two pumps configuring the twin pump makes it possible to simply double the pump lifetime.
  • a reference value is determined for performance difference between the two pumps configuring the twin pump. Further, positional relationship between the suction port and the discharge port, a distance between the suction port and the discharge port, and the like are preferably set to the same as those of the single pump in terms of installation and operation of the pump. Therefore, PTL 1 discloses a technique in which two pumps configuring a twin pump are rotated in directions opposite to each other, to suppress performance difference between the two pumps. In PTL 1, since the pumps rotated in the opposite directions are used, it is possible to minimize the performance difference. However, it is necessary to fabricate two types pumps different in structure, which disadvantageously increases design/manufacturing/management costs and stock.
  • PTL 2 discloses a technique in which a passage is suitably designed to suppress performance difference between two pumps different in shape.
  • rotary shafts of the two pumps are arranged such that the rotary shafts of the two pumps are located at positions symmetrical about a line connecting a center of a suction port and a center of a discharge port. Therefore, it is considered that efficiency of the pumps is sacrificed.
  • An aspect of the present invention is made to solve such issues, and an object thereof is to provide a pump casing eliminating a disadvantage that the design/manufacturing/management costs are increased.
  • a pump casing used for a pump apparatus to transfer a liquid includes: a first pump casing; a first suction passage portion connected to the first pump casing; a first discharge passage portion connected to the first pump casing; a second pump casing; a second suction passage portion connected to the second pump casing; a second discharge passage portion connected to the second pump casing; a suction branching portion connected to the first suction passage portion and the second suction passage portion; and a discharge merging portion connected to the first discharge passage portion and the second discharge passage portion, in which the first pump casing and the second pump casing have substantially a same shape, and the first discharge passage portion and the second discharge passage portion have substantially a same shape.
  • the first pump casing and the second pump casing have substantially the same shape, and the first discharge passage portion and the second discharge passage portion have substantially the same shape. Therefore, an impeller, a casing, and the like configuring the pump, and the discharge passage portion can be made common to the two pumps.
  • the two pumps can use a motor of the same rotation direction, which makes it possible to make a rotating body common to the two pumps. Accordingly, it is possible to provide the pump casing that eliminates a disadvantage of increase in design/manufacturing/management costs and a disadvantage of increase in stock.
  • the first discharge passage portion and the first pump casing are separately independent of each other and/or the second discharge passage portion and the second pump casing are separately independent of each other.
  • a cross-sectional shape of a passage of the first discharge passage portion at a connection portion between the first discharge passage portion and the discharge merging portion is a rectangular shape
  • a cross-sectional shape of a passage of the second discharge passage portion at a connection portion between the second discharge passage portion and the discharge merging portion is a rectangular shape
  • a pump apparatus includes: a first electric motor; a first rotary shaft coupled to the first electric motor; a first impeller fixed to the first rotary shaft and housed in the first pump casing; a second electric motor; a second rotary shaft coupled to the second electric motor; a second impeller fixed to the second rotary shaft and housed in the second pump casing; and the pump casing according to any one of the first to third aspects.
  • Fig. 1 is a schematic view illustrating an embodiment of a pump casing 18 according to the present invention.
  • the pump casing 18 is used for a pump apparatus 16 to transfer a liquid.
  • One pump casing 18 includes a first pump casing 181, a first suction passage portion 201 connected to the first pump casing 181, and a first discharge passage portion 221 connected to the first pump casing 181.
  • the pump casing 18 further includes a second pump casing 182, a second suction passage portion 202 connected to the second pump casing 182, and a second discharge passage portion 222 connected to the second pump casing 182.
  • the pump casing 18 further includes a suction branching portion 24 connected to the first suction passage portion 201 and the second suction passage portion 202, and a discharge merging portion 26 connected to the first discharge passage portion 221 and the second discharge passage portion 222.
  • the first pump casing 181, the first suction passage portion 201, the first discharge passage portion 221, the second pump casing 182, the second suction passage portion 202, the second discharge passage portion 222, the suction branching portion 24, and the discharge merging portion 26 are integrally formed as a casting. Some of these portions, for example, the first discharge passage portion 221, the second discharge passage portion 222, and the discharge merging portion 26 may be manufactured as castings other than the other portions. In other words, the first discharge passage portion 221 and the first pump casing 181 can be formed as an independent part, and/or the second discharge passage portion 222 and the second pump casing 182 can be formed as an independent part.
  • the first pump casing 181 and the second pump casing 182 substantially have the same shape.
  • the first discharge passage portion 221 and the second discharge passage portion 222 substantially have the same shape.
  • the first pump casing and the second pump casing have substantially the same shape, and the first discharge passage portion and the second discharge passage portion have substantially the same shape. Therefore, an impeller, a casing, and the like configuring the pump, and the discharge passage portion can be made common to the two pumps.
  • the two pumps can use a motor of the same rotation direction, which makes it possible to make a rotation body common to the two pumps.
  • the pump casing that eliminates a disadvantage of increase in design/manufacturing/management costs and a disadvantage of increase in stock that occur in a case where the shapes are different. Since the shapes are the same as each other, design data and parts of one of the pumps can be diverted in a design stage, a manufacturing stage, and a maintenance stage, which makes it possible to reduce the cost in each of the stages.
  • the suction branching portion 24 corresponds to a section from a suction port 20 to a part branched to the first suction passage portion 201 and the second suction passage portion 202. More specifically, the suction branching portion 24 corresponds to a section from the suction port 20 to a start end part 58 of the first suction passage portion 201, and a section from the suction port 20 to a start end part 60 of the second suction passage portion 202.
  • the discharge merging portion 26 corresponds to a section from a part where the first discharge passage portion 221 and the second discharge passage portion 222 merge with each other to a discharge port 22.
  • the discharge merging portion 26 corresponds to a section from a terminal end part 281 of the first discharge passage portion 221 to the discharge port 22, and a section from a terminal end part 282 of the second discharge passage portion 222 to the discharge port 22.
  • the suction port 20 of the pump apparatus 16 is a connection portion between the pump apparatus 16 and a pipe (not illustrated) on a suction side of the pump apparatus 16.
  • the discharge port 22 of the pump apparatus 16 is a connection portion between the pump apparatus 16 and a pipe (not illustrated) on a discharge side of the pump apparatus 16.
  • the first discharge passage portion 221 and the first pump casing 181 can be formed as an independent part, and/or the second discharge passage portion 222 and the second pump casing 182 can be formed as an independent part.
  • a boundary between the first discharge passage portion 221 and the first pump casing 181 is, for example, a connection portion 284 illustrated in Fig. 1 .
  • a boundary between the second discharge passage portion 222 and the second pump casing 182 is, for example, a connection portion 285 illustrated in Fig. 1 .
  • Positions of the connection portion 284 and the connection portion 285 are illustrative.
  • the boundaries may be provided at positions close to the discharge port 22 more than the positions of the connection portion 284 and the connection portion 285, or the boundaries may be provided at positions far from the discharge port 22 more than the positions of the connection portion 284 and the connection portion 285.
  • the pump apparatus 16 includes a first pump apparatus 161 and a second pump apparatus 162.
  • the first pump apparatus 161 and the second pump apparatus 162 may have the same configuration or different configurations. In terms of compatibility, however, the first pump apparatus 161 and the second pump apparatus 162 preferably have the same configuration.
  • the first pump apparatus 161 and the second pump apparatus 162 substantially have the same configuration.
  • a first impeller 51, the first pump casing 181, and the first discharge passage portion 221 respectively have the same dimensional shapes as a second impeller 52, the second pump casing 182, and the second discharge passage portion 222.
  • a rotation direction 54 of the first impeller 51 is the same as a rotation direction 56 of the second impeller 52.
  • the dimensional shape of the first suction passage portion 201 and the dimensional shape of the second suction passage portion 202 are slightly different from each other.
  • the first pump apparatus 161 and the second pump apparatus 162 are centrifugal pumps; however, the first pump apparatus 161 and the second pump apparatus 162 are not limited to the centrifugal pumps as long as the first pump apparatus 161 and the second pump apparatus 162 are non-positive displacement pumps.
  • the first pump apparatus 161 and the second pump apparatus 162 may be turbine pumps, axial-flow pumps, or mixed flow pumps.
  • Fig. 2 is a schematic view illustrating an embodiment of the first pump apparatus 161.
  • the first pump apparatus 161 includes a first electric motor 101, a first rotary shaft 121 coupled to the first electric motor 101, and the first impeller 51 that is fixed to the first rotary shaft 121 and is housed in the first pump casing 181.
  • the second pump apparatus 162 also have a second electric motor, a second rotary shaft coupled to the second electric motor, and the second impeller 52 that is fixed to the second rotary shaft and is housed in the second pump casing 182, as with the first pump apparatus 161.
  • the first impeller 51 is a centrifugal impeller.
  • the rotary shaft 121 is rotatably supported by a bearing (not illustrated).
  • the rotary shaft 121 and the first impeller 51 are integrally rotatable.
  • the rotary shaft 121 and the first impeller 51 are rotated by the electric motor 101.
  • a liner ring 102 is disposed around a fluid inlet 51a of the first impeller 51.
  • the liner ring 102 is fixed to the first pump casing 181.
  • a casing cover 122 is disposed between the electric motor 101 and the first pump casing 181. An opening at an upper part of the first pump casing 181 is closed by the casing cover 122.
  • the electric motor 101 is fixed to the casing cover 122.
  • the first pump casing 181 and the casing cover 122 are formed as castings.
  • a shaft sealing device 15 sealing a gap between the rotary shaft 121 and the casing cover 122 is disposed on a rear side of the first impeller 51.
  • the shaft sealing device 15 is held by the casing cover 122. Examples of the shaft sealing device 15 include a mechanical seal.
  • the blank flange (not illustrated) is disposed at a position of the casing cover 122 at maintenance or the like.
  • the blank flange is attached by using screw holes 62 (see Fig. 3 ) circumferentially arranged for attachment of the casing cover 122.
  • the blank flange has a disk shape, and includes, on an outer edge of the blank flange, attachment holes circumferentially arranged at positions corresponding to the screw holes 62.
  • the pump casing 18 includes the suction branching portion 24 including the suction port 20, and the discharge merging portion 26 including the discharge port 22.
  • the first impeller 51 is disposed inside the first pump casing 181.
  • the suction port 20 and the discharge port 22 are arranged on one straight line.
  • the pump apparatus 16 in which the suction port 20 and the discharge port 22 are arranged on one straight line is called an inline pump apparatus.
  • two inline pumps are arranged in parallel, one suction port and one discharge port are connected to the two inline pumps, and the two inline pumps share one suction port and one discharge port. When the two inline pumps share one suction port and one discharge port, these pumps configure one twin pump as a whole.
  • a difference between one inline pump as a twin pump and two inline pumps (two single pumps) arranged in parallel is described.
  • discharge ports of the single pumps are connected to respective pipes on a discharge side, and the two pipes are then merged to form one pipe on a downstream side.
  • one pipe is branched into two pipes, and the two pipes are connected to suction ports of the respective single pumps.
  • twin pump two discharge passage portions are merged at the discharge merging portion 26 on the discharge side, and the merged passage portion is connected to a pipe at the discharge port 22 of the twin pump.
  • a pipe is connected to the suction port 20 of the pump, and is then branched into two suction passage portions through the suction branching portion 24.
  • the liquid flows into the pump casing 18 from the suction port 20. More specifically, the liquid flows into the first suction passage portion 201 from the suction port 20, and then flows into the fluid inlet 51a of the first impeller 51 through the first suction passage portion 201.
  • the rotating first impeller 51 applies velocity energy to the liquid, and the velocity energy of the liquid flowing through the first pump casing 181 is converted into pressure.
  • the pressurized liquid is discharged from the pump casing 18 through the discharge port 22.
  • the discharge merging portion 26 includes an on-off valve 28.
  • the on-off valve 28 closes the discharge passage portion connected to the stopped pump apparatus based on operation states of the first pump apparatus 161 and the second pump apparatus 162.
  • the on-off valve 28 is moved to a position 282 illustrated by a dotted line by hydraulic pressure from the first discharge passage portion 221, to close the second discharge passage portion 222.
  • the on-off valve 28 is moved to a position 281 illustrated by a dashed line by hydraulic pressure from the second discharge passage portion 222, to close the first discharge passage portion 221.
  • the on-off valve 28 is moved to an intermediate position 283 illustrated by a solid line by hydraulic pressure from the first discharge passage portion 221 and hydraulic pressure from the second discharge passage portion 222.
  • Figs. 3 to 5 each illustrate a configuration of the single pump casing 18.
  • Fig. 3 is a top view of the pump casing 18.
  • Fig. 4 is a perspective view of the pump casing 18.
  • Fig. 5 is a bottom view of the pump casing 18.
  • Figs. 3 to 5 each illustrate the pump casing 18 in a state where the components other than the pump casing 18, namely, the first electric motor 101, the first rotary shaft 121, the first impeller 51, the second electric motor, the second rotary shaft, the second impeller 52, and the like are detached from the pump apparatus 16.
  • the suction port 20 is provided in a suction flange 34.
  • the suction flange 34 is to connect the pump casing 18 to a pipe.
  • the discharge port 22 is provided in a discharge flange 36.
  • the discharge flange 36 is to connect the pump casing 18 to a pipe.
  • the pump casing 18 can include leg portions 46 and 48 provided in the first pump casing 181 and the second pump casing 182. The reason why the leg portions 46 and 48 are provided at these positions is because a bottom part of the first pump casing 181 and a bottom part of the second pump casing 182 are located at the lowest positions in the pump apparatus 16 as illustrated in Fig. 2 .
  • a cross-sectional shape 64 of the passage of the first discharge passage portion 221 at the connection portion 281 between the first discharge passage portion 221 and the discharge merging portion 26 can be formed in a rectangular shape, and/or the cross-sectional shape 64 of the passage of the second discharge passage portion 222 at the connection portion 282 between the second discharge passage portion 222 and the discharge merging portion 26 can be formed in a rectangular shape.
  • Fig. 6 is a diagram illustrating the terminal end part 282 (connection portion 282) of the second discharge passage portion 222 as viewed from a direction 66 illustrated in Fig. 3 .
  • the cross-sectional shape 64 of the passage of the first discharge passage portion 221 at the terminal end part 281 and the cross-sectional shape 64 of the passage of the second discharge passage portion 222 at the terminal end part 282 are both formed in a rectangular shape.
  • an outer shape of the second discharge passage portion 222 is a circular tube shape
  • the cross-sectional shape of the passage inside the second discharge passage portion 222 is a circular shape.
  • the outer shape of the second discharge passage portion 222 is changed from the circular tube shape to a rectangular tube shape from the connection portion 285 between the second pump casing 182 and the second discharge passage portion 222 toward the connection portion 282 between the discharge merging portion 26 and the second discharge passage portion 222.
  • the cross-sectional shape of the passage inside the second discharge passage portion 222 is also changed from the circular shape to the rectangular shape.
  • the shape of the first discharge passage portion 221 is also changed in a manner similar to the shape of the second discharge passage portion 222.
  • Fig. 7 illustrates a case where a cross-sectional shape 68 of the inner diameter of the second discharge passage portion 222 connected to the discharge merging portion 26 is a circular shape.
  • Fig. 7 is a diagram illustrating the terminal end part 282 of the second discharge passage portion 222 as viewed from the direction 66 in Fig. 3 in the case where the cross-sectional shape 68 of the inner diameter is the circular shape.
  • Figs. 8 to 10 illustrate comparative examples of the present invention. These comparative examples are examples in which the first pump casing and the second pump casing do not have the same shape, or the first discharge passage portion and the second discharge passage portion do not have the same shape.
  • Fig. 8 illustrates an example in which a first discharge passage portion 223 and a second discharge passage portion 224 do not have the same shape.
  • a first pump casing 183 and a second pump casing 184 have the same shape.
  • Rotary shafts 74 and 76 of the two pumps are arranged such that the rotary shafts 74 and 76 of the two pumps are located at positions symmetrical about a line 72 connecting a center of the suction port 20 and a center of the discharge port 22.
  • rotary shafts 74 and 76 of the two pumps are arranged such that an intersection 84 between the line 72 and a line 78 connecting the rotary shaft 74 and the rotary shaft 76 is equally distanced from the center of the suction port 20 and the center of the discharge port 22.
  • Fig. 8 illustrates that the intersection 84 is equally distanced from the center of the suction port 20 and the center of the discharge port 22. In other words, a distance 88 and a distance 90 are equal to each other.
  • the discharge merging portion 26 is disposed so as to be symmetrical about the line 72 as in Fig. 3 .
  • the first pump casing 183, the second pump casing 184, and the discharge merging portion 26 are arranged so as to have such symmetricity, the fluid flowing from the second discharge passage portion 224 on a left side into the discharge merging portion 26 is large in pressure loss inside the discharge merging portion 26.
  • performance difference occurs between the right and left pumps.
  • the second pump casing 184 on the left side is first disposed at a position where the pressure loss is small, and the discharge merging portion 26 and the first pump casing 183 are suitably disposed.
  • the first pump casing 181 and the second pump casing 182 have substantially the same shape, and the first discharge passage portion 221 and the second discharge passage portion 222 have substantially the same shape.
  • performance of the two pumps can be advantageously brought close to each other irrespective of a diameter and a shape of the passage.
  • performance difference occurs between the two pumps with high possibility.
  • an angle of the discharge merging portion 26 is inclined slightly, for example, by 15 degrees in a clockwise direction in Fig. 8 .
  • a contact surface between the first discharge passage portion 223 and the discharge merging portion 26 is parallel.
  • the fluid from the first discharge passage portion 223 flows into the connection portion 281 (see Fig. 1 ) in a perpendicular direction.
  • the discharge merging portion 26 is not changed in shape but is slightly inclined in the clockwise direction.
  • Inner walls 80 (see Fig. 3 together) of the discharge merging portion 26 illustrated in Fig. 8 indicate positions before the inclination, and inner walls 82 of the discharge merging portion 26 illustrated in Fig. 8 indicate positions after the inclination.
  • the outer shape of the discharge merging portion 26 after the inclination is not illustrated in Fig. 8 for clarity of the drawing.
  • the shape of the first discharge passage portion 223 is changed so as to match with the inclined discharge merging portion 26.
  • the rotary shaft 74 and the rotary shaft 76 can be disposed so as to be equally distanced from the intersection 84 as a center of the whole apparatus. This stabilizes a centroid position.
  • Fig. 8 The characteristics in Fig. 8 are organized as follows. (i) The rotary shafts 74 and 76 of the two pumps are located at the positions substantially symmetrical about the line 72 connecting the suction port 20 and the discharge port 22. (ii) The intersection 84 between the line 72 and the line 78 connecting the rotary shaft 74 and the rotary shaft 76 is substantially equally distanced from the suction port 20 and the discharge port 22.
  • the discharge merging portion 26 is disposed at the position that is rotated from the position symmetrical about the line 72 in the clockwise direction (in other words, toward first pump casing 183 of first pump when pressure loss of first pump out of first pump and second pump is large) or in the counterclockwise direction (in other words, toward second pump casing 184 of second pump when pressure loss of second pump out of first pump and second pump is large) with a base part 92 of the discharge merging portion 26 as a rotation center.
  • Fig. 9 illustrates a second comparative example.
  • a first discharge passage portion 2231 is disposed substantially in parallel with the line 72 in Fig. 9 .
  • a first pump casing 1831 is disposed at a position close to the line 72 more than the first pump casing 183 illustrated in Fig. 8 .
  • the first pump casing 183 is moved toward the intersection 84 substantially in parallel with the line 78 connecting the rotary shaft 74 and the rotary shaft 76. Note that the first pump casing 183 and the first discharge passage portion 223 illustrated in Fig.
  • FIG. 9 are the same as the first pump casing 183 and the first discharge passage portion 223 illustrated in Fig. 8 .
  • the first pump casing 183 and the first discharge passage portion 223 illustrated in Fig. 8 are illustrated again in order to illustrate change of the first pump casing 183 and the first discharge passage portion 223.
  • Disposing the first discharge passage portion 2231 substantially in parallel with the line 72 means that the arrangement of the first pump casing 1831 gets close to the arrangement of the above-described single pump. As a result, an angle of the passage of the fluid flowing from the first pump casing 1831 into the discharge merging portion 26 becomes gentle inside the discharge merging portion 26. Therefore, pressure loss of the first pump casing 1831 is reduced.
  • the arrangement illustrated in Fig. 9 can be used.
  • the characteristics in Fig. 9 are organized as follows.
  • the first discharge passage portion 2231 is located at a position close to the line connecting the suction port 20 and the discharge port 22 more than the rotary shaft 74 of the first pump, and the first discharge passage portion 2231 is substantially parallel to the line connecting the suction port 20 and the discharge port 22.
  • Fig. 10 illustrates a third comparative example.
  • a first discharge passage portion 2232 is made longer than the second discharge passage portion 224 in Fig. 10 .
  • the first discharge passage portion 223 and the first pump casing 183 illustrated in Fig. 10 are rotated around the rotary shaft 74 in the counterclockwise direction, and are then moved in a positive X direction and a positive Y direction such that an end part of the first discharge passage portion 223 is located at the position of the discharge merging portion 26.
  • Fig. 10 illustrates a first pump casing 1832 and the first discharge passage portion 2232 that are the first discharge passage portion 223 and the first pump casing 183 rotated by 29 degrees in the counterclockwise direction and then moved in the positive X direction and the positive Y direction.
  • first discharge passage portion 2232 is longer than the second discharge passage portion 224, it is possible to gently expand the diameter of the passage of the first discharge passage portion 2232 in a direction from the first pump casing 1832 toward the discharge merging portion 26, as compared with the second discharge passage portion 224.
  • the first discharge passage portion 2232 is relatively small in an expansion amount of the diameter of the passage per unit length (in other words, expansion ratio). Therefore, pressure loss caused by abrupt expansion is reduced. As a result, performance of the first pump on the right side is improved to reduce the performance difference from the second pump on the left side.
  • Fig. 10 The characteristics in Fig. 10 are organized as follows. (i) When pressure loss of the first pump out of the first pump and the second pump is large, the length of the first discharge passage portion 2232 is made longer than the length of the second discharge passage portion 224.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP22177040.7A 2021-06-07 2022-06-02 Pumpengehäuse Pending EP4102076A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2021095049A JP2022187176A (ja) 2021-06-07 2021-06-07 ポンプケーシング

Publications (1)

Publication Number Publication Date
EP4102076A1 true EP4102076A1 (de) 2022-12-14

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Family Applications (1)

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EP22177040.7A Pending EP4102076A1 (de) 2021-06-07 2022-06-02 Pumpengehäuse

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JP (1) JP2022187176A (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU503228B1 (de) 2022-12-21 2024-06-21 Wilo Se Doppelpumpe mit Isolierverkleidung und zugehöriges Montageverfahren

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2434454Y (zh) * 2000-07-18 2001-06-13 上海凯泉泵业（集团）有限公司 单级单吸立式双联离心泵机组
EP2161455A1 (de) 2008-09-04 2010-03-10 Grundfos Management A/S Doppelpumpe
DE102014006258A1 (de) * 2014-04-30 2015-11-05 Wilo Se Verfahren zur Regelung eines Pumpensystems und geregeltes Pumpensystem
WO2018137019A1 (en) 2017-01-27 2018-08-02 S. A. Armstrong Limited Dual body variable duty performance optimizing pump unit
WO2020113113A1 (en) * 2018-11-28 2020-06-04 Bjm Pumps Llc In-line pumping apparatus, system and method for increasing liquid flow in gravity networks

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2434454Y (zh) * 2000-07-18 2001-06-13 上海凯泉泵业（集团）有限公司 单级单吸立式双联离心泵机组
EP2161455A1 (de) 2008-09-04 2010-03-10 Grundfos Management A/S Doppelpumpe
DE102014006258A1 (de) * 2014-04-30 2015-11-05 Wilo Se Verfahren zur Regelung eines Pumpensystems und geregeltes Pumpensystem
WO2018137019A1 (en) 2017-01-27 2018-08-02 S. A. Armstrong Limited Dual body variable duty performance optimizing pump unit
WO2020113113A1 (en) * 2018-11-28 2020-06-04 Bjm Pumps Llc In-line pumping apparatus, system and method for increasing liquid flow in gravity networks

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU503228B1 (de) 2022-12-21 2024-06-21 Wilo Se Doppelpumpe mit Isolierverkleidung und zugehöriges Montageverfahren
EP4390140A1 (de) 2022-12-21 2024-06-26 Wilo Se Doppelpumpe mit isolierverkleidung und zugehöriges montageverfahren

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