CN116608131A - Marine bidirectional transverse inclination adjusting pump - Google Patents
Marine bidirectional transverse inclination adjusting pump Download PDFInfo
- Publication number
- CN116608131A CN116608131A CN202310556642.9A CN202310556642A CN116608131A CN 116608131 A CN116608131 A CN 116608131A CN 202310556642 A CN202310556642 A CN 202310556642A CN 116608131 A CN116608131 A CN 116608131A
- Authority
- CN
- China
- Prior art keywords
- main shaft
- shaft
- pump
- bearing
- sleeve
- 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
Links
- 230000002457 bidirectional effect Effects 0.000 title claims abstract description 11
- 238000007789 sealing Methods 0.000 claims abstract description 34
- 230000007704 transition Effects 0.000 claims abstract description 29
- 230000005540 biological transmission Effects 0.000 claims abstract description 28
- 230000007246 mechanism Effects 0.000 claims abstract description 15
- 210000004907 gland Anatomy 0.000 claims description 31
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 22
- 230000000712 assembly Effects 0.000 claims description 15
- 238000000429 assembly Methods 0.000 claims description 15
- 238000013461 design Methods 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 21
- 239000003638 chemical reducing agent Substances 0.000 description 5
- 238000012423 maintenance Methods 0.000 description 5
- 238000009434 installation Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 240000008866 Ziziphus nummularia Species 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
- 239000013049 sediment Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
-
- 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
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/043—Shafts
-
- 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
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
-
- 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
- F04D29/06—Lubrication
- F04D29/061—Lubrication especially adapted for liquid pumps
-
- 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
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/106—Shaft sealings especially adapted for liquid pumps
-
- 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
- F04D29/18—Rotors
- F04D29/181—Axial flow rotors
- F04D29/183—Semi axial flow rotors
-
- 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
- F04D29/18—Rotors
- F04D29/185—Rotors consisting of a plurality of wheels
-
- 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
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/528—Casings; Connections of working fluid for axial pumps especially adapted for liquid pumps
-
- 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
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/548—Specially adapted for liquid pumps
-
- 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
- F04D29/60—Mounting; Assembling; Disassembling
- F04D29/64—Mounting; Assembling; Disassembling of axial pumps
- F04D29/648—Mounting; Assembling; Disassembling of axial pumps especially adapted for liquid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D3/00—Axial-flow pumps
Abstract
The utility model discloses a marine bidirectional transverse inclination adjusting pump, which comprises: the pump shell is characterized in that a pump cavity in the pump shell is divided into a direct current cavity and a driving cavity through a transmission shaft seat; the two direct current transition sections and the two inlet and outlet sections are respectively arranged at two sides of the pump shell; the main shaft is arranged in the pump cavity, and the middle part of the main shaft is arranged in the driving cavity; the left end and the right end of the main shaft are arranged at the inner sides of the inlet and outlet sections, the left end and the right end of the main shaft are provided with cover sealing components, and rib plates are arranged between the cover sealing components and the inlet and outlet sections; two groups of impellers are arranged on the inner side of the direct current transition section; the blades are half-axis flow symmetrical blades; the auxiliary shaft is arranged in the driving cavity, the axis of the auxiliary shaft is vertical to the axis of the main shaft, and the auxiliary shaft is in transmission connection with the main shaft through a transmission mechanism; and the motor is arranged on the pump shell, and the output end of the motor is in transmission connection with the auxiliary shaft. The utility model adopts the symmetrical design of the two-stage impeller mechanism, improves the pump body lift, simultaneously ensures that the pump body has good performance in forward rotation and reverse rotation, and meets the use requirement of the ship body.
Description
Technical Field
The utility model relates to the technical field of ship equipment, in particular to a bidirectional transverse inclination adjusting pump for a ship.
Background
In recent years, with the rapid development of offshore wind power industry, a large number of auxiliary work vessels around wind power operations, such as wind power installation vessels, pile driving vessels, operation and maintenance vessels, crane vessels, submarine cable laying vessels, submarine trenching vessels, and the like, have been developed.
As the name implies, the transverse tilt adjusting pump is used for adjusting transverse tilt of the crane ship when wind power equipment is lifted, and is one of the most critical equipment of the crane ship, whether the transverse tilt adjusting pump can reliably operate is directly determined, and whether the crane ship can normally operate or not.
An angular direct-connection type bidirectional axial flow pump provided by Chinese patent No. 210509605U comprises a motor, a coupler, an impeller, a pump shell and a speed reducer. The pump shell is an equal-diameter straight through pipe, and the pump shell which is transversely arranged in the axial direction is positioned and arranged at the bottom end of the motor to form an inverted T-shaped connecting structure. The speed reducer is an angular transmission mechanism, the vertical end of the speed reducer is positioned and installed in an upward inner hole in the middle section of the pump shell, the shaft end extending outwards from the short shaft is connected with the corresponding end of the coupler, and the other end of the coupler is connected with the output shaft end of the motor. The impeller adopts a symmetrical wing-shaped structure, and is positioned and installed on the shaft end of the long shaft of the speed reducer, so that a fixed-shaft rotating structure of the impeller driven by the motor in an angular direction is formed.
However, in the scheme, the axial flow pump adopts a single-stage structure, the pump set lift is low, and the requirements of bilge water and ballast water of a large ship on the outboard side are difficult to meet. Meanwhile, the impeller is positioned and arranged on the shaft end of the long shaft extending outwards of the speed reducer, so that the performance of the pump is unequal during forward rotation and reverse rotation, the performance requirement of hull adjustment cannot be met, and the efficiency of hull adjustment is affected.
In view of this, there is an urgent need to improve the structure of the bi-directional transverse pump for a ship in the prior art, so as to improve the lift of the transverse pump for a ship and enable the pump to have the performance of meeting the regulation requirement of the ship body when the pump rotates forward and backward.
Disclosure of Invention
The utility model aims to solve the technical problems that the existing marine bidirectional transverse pump has small working flow, low lift, unequal forward rotation performance and reverse rotation performance, and is difficult to meet the performance requirement of ship body adjustment.
In order to solve the technical problems, the technical scheme adopted by the utility model is as follows:
a bi-directional trim pump for a ship, comprising:
the pump comprises a pump shell, wherein a pump cavity is arranged in the pump shell, a transmission shaft seat is arranged in the pump cavity, and the transmission shaft seat divides the pump cavity into a direct current cavity and a driving cavity; the direct current cavity is in a straight pipe shape, and a direct current cavity opening is respectively arranged at the left end and the right end of the direct current cavity;
the two direct current transition sections are annular and are respectively arranged on the direct current cavity openings and detachably connected with the pump shell;
the two inlet and outlet sections are annular and are respectively arranged on one side of the direct current transition section, which is far away from the pump shell;
the main shaft is arranged in the pump cavity, and the middle part of the main shaft is arranged in the driving cavity; the left end and the right end of the main shaft are arranged on the inner sides of the inlet and outlet sections, the left end and the right end of the main shaft are provided with sealing cover assemblies, and rib plates are arranged between the sealing cover assemblies and the inlet and outlet sections; the main shaft is arranged on the transmission shaft seat and is in sealing connection with the transmission shaft seat through a sealing assembly;
two sets of impellers sleeved on the main shaft; the impeller is arranged in the direct current transition section; the blades of the impeller are semi-axis flow symmetrical blades, the left end and the right end of each blade are respectively provided with a water facing surface, and the two water facing surfaces are symmetrically arranged by taking the central axis of each blade as an axis;
a countershaft disposed within the drive chamber; the axis of the auxiliary shaft is perpendicular to the axis of the main shaft and is connected with the main shaft through a transmission mechanism;
and the motor is arranged on the pump shell, and the output end of the motor is in transmission connection with the auxiliary shaft.
In the above technical scheme, preferably, the transmission shaft seat is T-shaped, and a vertical part of the transmission shaft seat is provided with a secondary shaft mounting hole to form a secondary shaft seat; the horizontal part is provided with a main shaft mounting hole to form a main shaft seat; the auxiliary shaft mounting hole is communicated with the main shaft mounting hole to form the driving cavity.
In the above technical solution, preferably, the auxiliary shaft is disposed in the auxiliary shaft mounting hole, and an auxiliary shaft bearing assembly is disposed between the auxiliary shaft and the auxiliary shaft mounting hole, and the auxiliary shaft bearing assembly includes:
the auxiliary shaft bearing sleeve is arranged in the auxiliary shaft mounting hole, and the upper end of the auxiliary shaft bearing sleeve upwards penetrates out of the auxiliary shaft mounting hole;
the auxiliary shaft bearing is sleeved on the auxiliary shaft and is arranged between the auxiliary shaft bearing sleeve and the auxiliary shaft;
the auxiliary shaft bearing gland is sleeved on the auxiliary shaft and is arranged on the top surface of the pump shell; a countershaft bearing lock nut is arranged between the countershaft bearing gland and the countershaft bearing;
the screw penetrates through the auxiliary shaft bearing gland and the auxiliary shaft bearing sleeve to be fixedly connected with the pump shell.
In the above technical solution, preferably, a set of spindle bearing assemblies is respectively disposed at the left and right ends of the spindle seat, two ends of the spindle respectively penetrate from the spindle bearing assemblies, and each set of spindle bearing assemblies includes:
one end of the main shaft bearing sleeve is inserted into the main shaft mounting hole, and the other end of the main shaft bearing sleeve is arranged on the end face of the main shaft seat;
the main shaft bearing is a pair of deep groove ball bearings sleeved on the main shaft, and the main shaft bearing is arranged between the main shaft bearing sleeve and the main shaft;
the main shaft bearing gland is arranged on one side of the main shaft bearing sleeve, which is far away from the main shaft seat; a main shaft bearing lock nut is arranged between the main shaft bearing gland and the main shaft bearing;
the screw penetrates through the main shaft bearing gland and the main shaft bearing sleeve and is fixed with the main shaft seat.
In the above technical solution, preferably, the transmission mechanism is a main shaft gear provided on the main shaft and a sub shaft gear provided on the sub shaft, and the main shaft gear is meshed with the sub shaft gear;
the main shaft and the auxiliary shaft are respectively provided with a main shaft gear adjusting sleeve and an auxiliary shaft gear adjusting sleeve, the main shaft gear adjusting sleeve is arranged between the main shaft gear and the main shaft bearing assembly, and the auxiliary shaft gear adjusting sleeve is arranged between the auxiliary shaft gear and the auxiliary shaft bearing.
In the above technical solution, preferably, the sealing assembly includes:
the main shaft sealing shaft sleeve is sleeved on the main shaft;
the framework oil seal is sleeved on the main shaft sealing shaft sleeve, one end of the main shaft bearing gland, which is close to the main shaft bearing lock nut, is provided with a framework oil seal groove, and the framework oil seal is arranged in the framework oil seal groove;
the mechanical seal is sleeved on the main shaft sealing shaft sleeve; a mechanical seal groove is formed in one end, far away from the main shaft bearing lock nut, of the main shaft bearing gland, and the mechanical seal is arranged in the mechanical seal groove;
the water throwing ring is sleeved on the spindle sealing shaft sleeve and is arranged on one side of the mechanical seal, which is far away from the spindle bearing gland, and is fixedly connected with the spindle bearing gland.
In the above technical solution, preferably, the cap assembly includes:
the racing dragon bearing is sleeved on the main shaft and is arranged on one side of the impeller, which is close to the inlet and outlet section; an end cover shaft sleeve is arranged between the sialon bearing and the main shaft;
the racing dragon bearing sleeve is sleeved on the racing dragon bearing and is arranged between the racing dragon bearing and the rib plate;
the sealing cover is arranged at one end of the main shaft far away from the main shaft seat, and the middle part of the sealing cover is fixed with the end face of the main shaft; the outer diameter of the sealing cover is matched with the outer diameter of the sialon bearing sleeve.
In the above technical solution, preferably, the main shaft gear is connected with the main shaft, the counter shaft gear is connected with the counter shaft, and the impeller is connected with the main shaft through symmetrically arranged double bonds.
In the above technical scheme, preferably, an impeller adjusting sleeve detachably connected is arranged on the inner wall of the direct current transition section, and the impeller adjusting sleeve is arranged opposite to the outer circumferential surface of the impeller.
In the above technical solution, preferably, an oil window is provided on a side surface of the pump casing; an oil drain port and a water drain port are arranged on the bottom surface of the pump shell, the oil window and the oil drain port are communicated with the driving cavity, and the water drain port is communicated with the direct-current cavity.
Compared with the prior art, the bi-directional transverse inclination adjusting pump for the ship provided by the utility model adopts a two-stage impeller mechanism, so that the lift of the pump is improved; the pump body adopts symmetrical design, the impeller is symmetrically distributed, the blades of the impeller adopt half-axial flow jujube core type symmetrical blades, the same performance meeting the adjustment requirement of the ship body can be provided when the pump body rotates positively and reversely, and the adjustment efficiency of the ship body is improved. The utility model optimizes the structure of the pump body, the pump body consists of a pump shell, two groups of direct current transition sections and two groups of inlet and outlet sections which are arranged on two sides of the pump shell, improves the installation convenience degree of the mechanisms such as a main shaft, an impeller, a sealing assembly, a sealing cover assembly and the like in a pump cavity, and simultaneously improves the convenience of maintenance and replacement of the components in the pump body.
Drawings
FIG. 1 is a schematic structure of a bi-directional trim pump for a ship in accordance with the present utility model;
FIG. 2 is a schematic view of the pump body according to the present utility model;
FIG. 3 is an enlarged schematic view of FIG. 2 at A;
FIG. 4 is an enlarged schematic view at B in FIG. 2;
FIG. 5 is an enlarged schematic view of FIG. 2 at C;
FIG. 6 is an enlarged schematic view of FIG. 2D;
FIG. 7 is a schematic view of the vane of the impeller of the present utility model;
fig. 8 is a schematic view of a conventional impeller blade.
The correspondence between the names and the reference numerals of the respective components in fig. 1 to 8 is as follows:
pump shell 1, direct current transition section 2, inlet and outlet section 3, main shaft 4, impeller 5, auxiliary shaft 6, motor 7,
a pump shell body 11, a pump seat 12, a transmission shaft seat 13,
a through-flow chamber 110, an oil window 112, an oil drain 113, a drain port 114,
a drive chamber 130, a sub-shaft seat 131, a main shaft seat 132,
the impeller adjusting sleeve 21, the rib plate 31,
spindle bearing assembly 41, seal assembly 42, spindle gear 43, spindle gear adjustment sleeve 44, cover assembly 45,
spindle bearing housing 411, spindle bearing 412, spindle bearing gland 413, spindle bearing lock nut 414,
spindle sealing sleeve 421, backbone oil seal 422, mechanical seal 423, water slinger 424,
the race-on bearing 451, the race-on bearing sleeve 452, the cover 453, the end cap sleeve 454,
a first water-facing surface 51, a second water-facing surface 52,
a countershaft bearing assembly 61, a countershaft gear 62, a countershaft gear adjustment sleeve 63,
a countershaft bearing sleeve 611, a countershaft bearing 612, a countershaft bearing gland 613.
Detailed Description
The utility model provides a bidirectional transverse tilting pump for a ship, which adopts a symmetrical design of a two-stage impeller mechanism, improves the pump body lift, ensures that the pump body has good performance in forward rotation and reverse rotation, and meets the use requirement of a ship body. The utility model is described in detail below with reference to the drawings and the detailed description.
As shown in fig. 1 to 8, the marine bidirectional transverse inclination adjusting pump provided by the utility model comprises a pump shell 1, two direct current transition sections 2, two inlet and outlet sections 3, a main shaft 4, two groups of impellers 5, a secondary shaft 6 and a motor 7.
The pump shell 1, the two direct current transition sections 2 and the two inlet and outlet sections 3 form a pump body, the main shaft 4 and the two groups of impellers 5 are arranged in the pump body, and the motor 7 is arranged on the pump body and drives the main shaft 4 to rotate through the auxiliary shaft 6 and the transmission mechanism.
The pump casing 1 includes a pump casing body 11 and a pump seat 12 for supporting the pump casing body 11, the pump casing body 11 is mountable on the pump seat 12, is connected to the hull through the pump seat 12, and is loaded by the pump seat 12 with the weight of the marine bi-directional roll adjustment pump.
A pump cavity is arranged in the pump shell body 11, a T-shaped transmission shaft seat 13 is arranged in the pump cavity, and a countershaft mounting hole is arranged on the vertical part of the transmission shaft seat 13 to form a countershaft seat 131; the horizontal part of the transmission shaft seat 13 is provided with a main shaft mounting hole to form a main shaft seat 132. The secondary shaft mounting hole is communicated with the primary shaft mounting hole to form a driving cavity 130, so that the transmission shaft seat 13 divides the pump cavity into a direct current cavity 110 and the driving cavity 130. The direct current cavity 110 is in a straight pipe shape, and a direct current cavity opening is respectively arranged at the left end and the right end of the direct current cavity 110.
The two direct current transition sections 2 are annular and are respectively arranged on the direct current cavity openings, and the two direct current transition sections 2 are detachably connected with the pump shell body 11.
The two inlet and outlet sections 3 are annular and are respectively arranged on one side of the direct current transition section 2, which is far away from the pump shell body 11. The two inlet and outlet sections 3 are used for connecting with pipelines on the ship body.
The main shaft 4 and the auxiliary shaft 6 are arranged on a transmission shaft seat 13 and are rotatably arranged in the pump cavity.
The middle part of the spindle 4 is disposed in the driving chamber 130 through a spindle mounting hole. The left and right ends of the spindle seat 132 are respectively provided with a group of spindle bearing assemblies 41, and the two ends of the spindle 4 respectively penetrate out of the spindle bearing assemblies 41, wherein each group of spindle bearing assemblies 41 comprises a spindle bearing sleeve 411, a spindle bearing 412 and a spindle bearing gland 413. One end of the spindle bearing housing 411 is inserted into the spindle mounting hole, and the other end of the spindle bearing housing 411 is disposed on the end surface of the spindle base 132. The main shaft bearing 412 is a pair of deep groove ball bearings sleeved on the main shaft 4, and the main shaft bearing 412 is arranged between the main shaft bearing housing 411 and the main shaft 4, so that the main shaft bearing 412 is prevented from directly contacting the main shaft seat 132 to cause abrasion of the main shaft seat 132, and the purpose of prolonging the service life of the pump shell body 11 is realized. The spindle bearing cover 413 is disposed on a side of the spindle bearing housing 411 away from the spindle base 132, and a spindle bearing lock nut 414 is disposed between the spindle bearing cover 413 and the spindle bearing 412. The screw penetrates the spindle bearing cover 413 and the spindle bearing housing 411 and is fixed to the spindle base 132.
The spindle 4 is sealingly connected to the spindle base 132 by a seal assembly 42. The sealing assembly 42 comprises a main shaft sealing shaft sleeve 421 sleeved on the main shaft 4, and a framework oil seal 422, a mechanical seal 423 and a water throwing ring 424 sleeved on the main shaft sealing shaft sleeve 421. A skeleton oil seal groove and a mechanical seal groove are respectively arranged on one end of the main shaft bearing gland 413, which is close to the main shaft bearing lock nut 414, and one end of the main shaft bearing gland 413, which is far away from the main shaft bearing lock nut 414, and a skeleton oil seal 422 and a mechanical seal 423 are respectively arranged on the skeleton oil seal groove and the mechanical seal groove. The water slinger 424 is arranged on one side of the mechanical seal 423 far away from the main shaft bearing gland 413, the water slinger 424 is fixed on the main shaft bearing gland 413, the water slinger 424 can generate centrifugal force when the main shaft 4 runs, and impurities such as sediment in seawater are prevented from entering the mechanical seal 424, so that the mechanical seal 424 is protected.
The spindle sealing sleeve 421 serves to protect the spindle 4, and further improves the sealability of the seal assembly 42 because the sleeve can more easily meet the requirements of high surface finish and accuracy than the shaft. The mechanical seal 423 can select single-end-face mechanical seal with an M74 type small spring structure, so that the condition that silt is clamped on the shaft sleeve and cannot move axially to cause seal failure is avoided. The backbone oil seal 422 serves as an auxiliary seal in the event of failure of the mechanical seal 423.
The auxiliary shaft 6 is arranged in the auxiliary shaft mounting hole of the auxiliary shaft seat 131, and an auxiliary shaft bearing assembly 61 is arranged between the auxiliary shaft 6 and the auxiliary shaft mounting hole. The auxiliary shaft bearing assembly 61 includes an auxiliary shaft bearing housing 611, an auxiliary shaft bearing 612 and an auxiliary shaft bearing gland 613. The auxiliary shaft bearing sleeve 611 is arranged in the auxiliary shaft mounting hole, and the upper end of the auxiliary shaft bearing sleeve 611 upwards penetrates out of the auxiliary shaft mounting hole. The counter bearing 612 is provided on the counter shaft 6, and is provided between the counter bearing housing 611 and the counter shaft 6. The auxiliary shaft bearing gland 613 is sleeved on the auxiliary shaft 6 and arranged on the top surface of the pump shell body 11. A counter bearing lock nut 613 is provided between the counter bearing gland 613 and the counter bearing 612 for locking the counter bearing 612. The screw penetrates the auxiliary shaft bearing gland 613 and the auxiliary shaft bearing sleeve 611 and is fixedly connected with the pump shell body 11.
The axis of the main shaft 4 is perpendicular to the axis of the auxiliary shaft 6, the main shaft 4 is provided with a main shaft gear 43, the auxiliary shaft 6 is provided with an auxiliary shaft gear 62, and the main shaft gear 43 is meshed with the auxiliary shaft gear 62 to form a transmission mechanism for driving the main shaft 4 by the auxiliary shaft 6. The main shaft gear 43 and the sub shaft gear 62 are bevel gears. The rotation of the motor 7 in the vertical direction is converted into the rotation in the horizontal direction through the meshed bevel gears so as to match the layout of the ship body pipelines, and meanwhile, the occupied space of the pump body is reduced. The tooth shape of the bevel gear adopts a circular arc tooth shape, and compared with an involute tooth shape, the circular arc tooth shape has stronger bearing capacity and can bear the impact of alternating load caused by frequent forward and reverse switching of the pump. The bevel gear can be matched with different modulus according to the requirement, and various different rotating speeds can be changed, so that the pump has various different performances.
In order to adjust the meshing gap between the tooth profiles of the main shaft gear 43 and the auxiliary shaft gear 62 to ensure reasonable running gap, a main shaft gear adjusting sleeve 44 and an auxiliary shaft gear adjusting sleeve 63 are respectively arranged on the main shaft 4 and the auxiliary shaft 6, the main shaft gear adjusting sleeve 44 is arranged between the main shaft gear 43 and the main shaft bearing assembly 41, and the auxiliary shaft gear adjusting sleeve 63 is arranged between the auxiliary shaft gear 62 and the auxiliary shaft bearing assembly 61.
The main shaft gear 43, the sub shaft gear 62, the main shaft bearing 412 and the sub shaft bearing 612 are rare lubrication, and an oil window 112 is provided on the side surface of the pump housing body 11, and the oil window 112 communicates with the drive chamber 130 for observing the oil level. An oil drain 113 and a water drain 114 are provided on the bottom surface of the pump housing body 11, the oil drain 113 is communicated with the driving chamber 130, and the water drain 114 is communicated with the direct current chamber 110, so as to facilitate maintenance and replacement of lubricating oil.
The motor 7 is mounted on the pump housing 1 and its output is in driving connection with the auxiliary shaft 6. In order to improve the stability of the motor 7 and adapt to motors with different specifications and sizes, a connecting frame and a motor transition section are arranged on the pump shell 1, the connecting frame is detachably connected with the motor transition section, and the motor 7 is arranged on the connecting frame through the motor transition section. The motor can be connected with the auxiliary shaft 6 through a pair of elastic pin couplings, and the elastic pin couplings are made of rubber materials and have good elastic sleeves, so that the impact caused by frequent switching of positive and negative rotation of the pump can be effectively buffered.
The left and right ends of the main shaft 4 are arranged on the inner side of the inlet and outlet section 3, and two groups of impellers 5 are sleeved on the main shaft 4. Cover assemblies 45 are arranged at the left end and the right end of the main shaft 4, and rib plates 31 are arranged between the cover assemblies 45 and the inlet and outlet sections 3. The closure assembly 45 includes a packing member 451, a packing member 452 and a closure 453. The racing dragon bearing 451 is sleeved on the main shaft 4, and the racing dragon bearing 451 is arranged on one side of the impeller 5, which is close to the inlet and outlet section 3. An end cover shaft sleeve 454 is arranged between the sialon bearing 451 and the main shaft 4 and is used for protecting the main shaft 4. The race-track bearing sleeve 452 is fitted over the race-track bearing 451, and is disposed between the race-track bearing 451 and the rib plate 31. The closing cap 453 sets up the one end that keeps away from the headstock at main shaft 4, and the external diameter of closing cap 453 and the external diameter looks adaptation of the race dragon bearing housing 452 for lock race dragon bearing 451 and race dragon bearing housing 452. The middle part of the cover 453 is fixed with the end face of the spindle 4, so that the cover 453 is ensured not to loosen when the spindle 4 rotates forward or backward.
The impeller 5 is arranged on the inner side of the direct current transition section 2, an impeller adjusting sleeve 21 which is detachably connected is arranged on the inner wall of the direct current transition section 2, and the impeller adjusting sleeve 21 is arranged opposite to the outer circumferential surface of the impeller 5. The blades of the impeller 5 are semi-axis flow symmetrical blades, the left and right ends of the blades are respectively provided with a first water-facing surface 51 and a second water-facing surface 52, and the first water-facing surface 51 and the second water-facing surface 52 are symmetrically arranged by taking the central axis a of the blades as a symmetrical axis.
Fig. 7 and 8 are schematic views showing the projection of the blades of the impeller of the present utility model and the blades of the conventional impeller on the outer circumferential surface of the impeller hub in a direction perpendicular to the outer circumferential surface of the impeller hub, respectively.
As shown in fig. 8, the upstream surfaces of the left and right ends of the blades of the conventional impeller are asymmetrically designed, and when the impeller is operated in the forward direction, the entire blade is at a positive attack angle, thereby generating lift force. However, in reverse operation, the entire blade is at a negative angle of attack, and sufficient lift force or even drag force is not generated, so that the pump efficiency is greatly reduced in reverse rotation, and the required performance is not achieved.
As shown in fig. 7, the first water facing surface 51 and the second water facing surface 52 of the vane are symmetrically designed in the present utility model, so that the vane always generates enough lift force under the positive attack angle no matter the vane rotates forward or backward, thereby ensuring that the pump can achieve the required performance.
The double-key connection between the main shaft gear 43 and the main shaft 4, between the auxiliary shaft gear 62 and the auxiliary shaft 6 and between the impeller 5 and the main shaft 4 are symmetrically arranged, so that the connection strength between the gear and the main shaft 4 or the auxiliary shaft 6 and between the impeller 5 and the main shaft 4 can be improved, the bearing capacity of keys and key grooves can be improved, and the keys and the key grooves are prevented from being damaged due to frequent forward and reverse rotation switching of the pump.
The working process of the utility model is as follows:
the motor 7 drives the auxiliary shaft 6 to rotate, the auxiliary shaft 6 drives the auxiliary shaft gear 62 to rotate, and the main shaft 4 is driven to rotate through the main shaft gear 43 meshed with the auxiliary shaft gear 62 to drive the impeller 5 to rotate, so that water at the inlet and outlet section 3 at one side flows to the inlet and outlet section 3 at the other side along the straight tubular direct-current cavity 110, and the ship body is adjusted to tilt. Because the pump body adopts a two-stage impeller mechanism consisting of two groups of impellers 5 which are symmetrically arranged, and the upper blades of the impellers 5 are half-axial-flow jujube-core type symmetrical blades, the same performance of the pump body can be ensured when the impellers 5 rotate positively and negatively.
Compared with the prior art, the marine bidirectional transverse inclination adjusting pump provided by the utility model has the following advantages:
(1) The two-stage impeller mechanism is adopted, so that the lift of the pump is improved; the two groups of impellers are symmetrically arranged, the blades of the impellers are half-shaft jujube-core symmetrical blades, no matter the impellers are in positive attack angles or reverse rotation, enough lift force can be always generated, and the pump can reach the required performance, so that the performance requirement of hull adjustment is always met, and the hull adjustment efficiency is improved;
(2) The pump body is provided with the direct-current transition section, the direct-current transition section is detachably connected with the pump shell, and the impeller is arranged on the inner side of the direct-current transition section, so that the impeller and the sealing mechanism are convenient to disassemble and assemble, the installation efficiency of the pump is improved, and the maintenance of the pump is convenient; an impeller adjusting sleeve which is detachably connected with the direct current transition section is arranged in the direct current transition section, the impeller adjusting sleeve is arranged opposite to the impeller, different impellers can be arranged and different adjustment sets can be replaced according to different performance requirements of the ship body, and the inner diameter of the adjusting sleeve and the outer diameter of the impeller keep a relatively fixed gap, so that the transition section is always universal; meanwhile, the impeller adjusting sleeve can be corroded or worn for replacement, so that the service life of the direct-current transition section is prolonged, and the maintenance cost of the pump body is reduced;
(3) The rib plates are arranged in the inlet and outlet sections and distributed along the inner walls of the inlet and outlet sections, so that the function of guide vanes is achieved, kinetic energy generated by rotation of the impeller can be converted into potential energy, namely pressure energy, and meanwhile, the sealing cover assembly is supported and reinforced, and the stability and bearing capacity of the pump body structure are improved.
The present utility model is not limited to the above-mentioned preferred embodiments, and any person who can learn the structural changes made under the teaching of the present utility model can fall within the scope of the present utility model if the present utility model has the same or similar technical solutions.
Claims (10)
1. A bi-directional trim pump for a ship, comprising:
the pump comprises a pump shell, wherein a pump cavity is arranged in the pump shell, a transmission shaft seat is arranged in the pump cavity, and the transmission shaft seat divides the pump cavity into a direct current cavity and a driving cavity; the direct current cavity is in a straight pipe shape, and a direct current cavity opening is respectively arranged at the left end and the right end of the direct current cavity;
the two direct current transition sections are annular and are respectively arranged on the direct current cavity openings and detachably connected with the pump shell;
the two inlet and outlet sections are annular and are respectively arranged on one side of the direct current transition section, which is far away from the pump shell;
the main shaft is arranged in the pump cavity, and the middle part of the main shaft is arranged in the driving cavity; the left end and the right end of the main shaft are arranged on the inner sides of the inlet and outlet sections, the left end and the right end of the main shaft are provided with sealing cover assemblies, and rib plates are arranged between the sealing cover assemblies and the inlet and outlet sections; the main shaft is arranged on the transmission shaft seat and is in sealing connection with the transmission shaft seat through a sealing assembly;
two sets of impellers sleeved on the main shaft; the impeller is arranged in the direct current transition section; the blades of the impeller are semi-axis flow symmetrical blades, the left end and the right end of each blade are respectively provided with a water facing surface, and the two water facing surfaces are symmetrically arranged by taking the central axis of each blade as an axis;
a countershaft disposed within the drive chamber; the axis of the auxiliary shaft is perpendicular to the axis of the main shaft and is connected with the main shaft through a transmission mechanism;
and the motor is arranged on the pump shell, and the output end of the motor is in transmission connection with the auxiliary shaft.
2. The marine bidirectional trim pump of claim 1, wherein the drive shaft mount is T-shaped with a secondary shaft mounting hole in a vertical portion thereof forming a secondary shaft mount; the horizontal part is provided with a main shaft mounting hole to form a main shaft seat; the auxiliary shaft mounting hole is communicated with the main shaft mounting hole to form the driving cavity.
3. The marine bi-directional trim pump of claim 2, wherein the secondary shaft is disposed within the secondary shaft mounting bore and a secondary shaft bearing assembly is disposed between the secondary shaft mounting bore, the secondary shaft bearing assembly comprising:
the auxiliary shaft bearing sleeve is arranged in the auxiliary shaft mounting hole, and the upper end of the auxiliary shaft bearing sleeve upwards penetrates out of the auxiliary shaft mounting hole;
the auxiliary shaft bearing is sleeved on the auxiliary shaft and is arranged between the auxiliary shaft bearing sleeve and the auxiliary shaft;
the auxiliary shaft bearing gland is sleeved on the auxiliary shaft and is arranged on the top surface of the pump shell; a countershaft bearing lock nut is arranged between the countershaft bearing gland and the countershaft bearing;
the screw penetrates through the auxiliary shaft bearing gland and the auxiliary shaft bearing sleeve to be fixedly connected with the pump shell.
4. A bi-directional trim pump for a vessel as defined in claim 3, wherein a set of spindle bearing assemblies are provided at left and right ends of the spindle base, respectively, and both ends of the spindle extend from the spindle bearing assemblies, respectively, each set of spindle bearing assemblies comprising:
one end of the main shaft bearing sleeve is inserted into the main shaft mounting hole, and the other end of the main shaft bearing sleeve is arranged on the end face of the main shaft seat;
the main shaft bearing is a pair of deep groove ball bearings sleeved on the main shaft, and the main shaft bearing is arranged between the main shaft bearing sleeve and the main shaft;
the main shaft bearing gland is arranged on one side of the main shaft bearing sleeve, which is far away from the main shaft seat; a main shaft bearing lock nut is arranged between the main shaft bearing gland and the main shaft bearing;
the screw penetrates through the main shaft bearing gland and the main shaft bearing sleeve and is fixed with the main shaft seat.
5. The marine bi-directional trim pump of claim 4, wherein said drive mechanism is a main shaft gear disposed on said main shaft and a counter shaft gear disposed on said counter shaft, said main shaft gear engaged with said counter shaft gear;
the main shaft and the auxiliary shaft are respectively provided with a main shaft gear adjusting sleeve and an auxiliary shaft gear adjusting sleeve, the main shaft gear adjusting sleeve is arranged between the main shaft gear and the main shaft bearing assembly, and the auxiliary shaft gear adjusting sleeve is arranged between the auxiliary shaft gear and the auxiliary shaft bearing.
6. The marine bi-directional trim pump of claim 4, wherein said seal assembly comprises:
the main shaft sealing shaft sleeve is sleeved on the main shaft;
the framework oil seal is sleeved on the main shaft sealing shaft sleeve, one end of the main shaft bearing gland, which is close to the main shaft bearing lock nut, is provided with a framework oil seal groove, and the framework oil seal is arranged in the framework oil seal groove;
the mechanical seal is sleeved on the main shaft sealing shaft sleeve; a mechanical seal groove is formed in one end, far away from the main shaft bearing lock nut, of the main shaft bearing gland, and the mechanical seal is arranged in the mechanical seal groove;
the water throwing ring is sleeved on the spindle sealing shaft sleeve and is arranged on one side of the mechanical seal, which is far away from the spindle bearing gland, and is fixedly connected with the spindle bearing gland.
7. The marine bi-directional trim pump of claim 2, wherein the cover assembly comprises:
the racing dragon bearing is sleeved on the main shaft and is arranged on one side of the impeller, which is close to the inlet and outlet section; an end cover shaft sleeve is arranged between the sialon bearing and the main shaft;
the racing dragon bearing sleeve is sleeved on the racing dragon bearing and is arranged between the racing dragon bearing and the rib plate;
the sealing cover is arranged at one end of the main shaft far away from the main shaft seat, and the middle part of the sealing cover is fixed with the end face of the main shaft; the outer diameter of the sealing cover is matched with the outer diameter of the sialon bearing sleeve.
8. The marine bi-directional trim pump of claim 1, wherein said main shaft gear is in double bond connection with said main shaft, said counter shaft gear is in double bond connection with said counter shaft, and said impeller is in double bond connection with said main shaft.
9. The marine bidirectional surge-tilt pump according to claim 1, wherein an impeller adjusting sleeve is detachably connected to an inner wall of the dc transition section, and the impeller adjusting sleeve is disposed opposite to an outer circumferential surface of the impeller.
10. The marine bi-directional trim pump of claim 1 wherein an oil window is provided on a side of said pump housing; an oil drain port and a water drain port are arranged on the bottom surface of the pump shell, the oil window and the oil drain port are communicated with the driving cavity, and the water drain port is communicated with the direct-current cavity.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310556642.9A CN116608131A (en) | 2023-05-15 | 2023-05-15 | Marine bidirectional transverse inclination adjusting pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310556642.9A CN116608131A (en) | 2023-05-15 | 2023-05-15 | Marine bidirectional transverse inclination adjusting pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116608131A true CN116608131A (en) | 2023-08-18 |
Family
ID=87684761
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310556642.9A Pending CN116608131A (en) | 2023-05-15 | 2023-05-15 | Marine bidirectional transverse inclination adjusting pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116608131A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09287594A (en) * | 1996-04-18 | 1997-11-04 | Mitsubishi Heavy Ind Ltd | Fan blade formed into point symmetrical blade profile |
| JP2000145695A (en) * | 1998-11-16 | 2000-05-26 | Kawasaki Heavy Ind Ltd | Axial flow blower |
| CN204126915U (en) * | 2014-09-14 | 2015-01-28 | 湖北省风机厂有限公司 | A kind of high thrust reversible tunnel jet blower |
| CN109826802A (en) * | 2019-03-25 | 2019-05-31 | 扬州大学 | A kind of Double-way axial flow pump installation with hiding rear guide vane structure |
| CN210509605U (en) * | 2019-08-27 | 2020-05-12 | 江苏振华泵业制造有限公司 | Angular direct-connected bidirectional axial-flow pump |
| CN112682315A (en) * | 2020-12-17 | 2021-04-20 | 武汉船用电力推进装置研究所（中国船舶重工集团公司第七一二研究所） | Bidirectional axial flow pump |
-
2023
- 2023-05-15 CN CN202310556642.9A patent/CN116608131A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09287594A (en) * | 1996-04-18 | 1997-11-04 | Mitsubishi Heavy Ind Ltd | Fan blade formed into point symmetrical blade profile |
| JP2000145695A (en) * | 1998-11-16 | 2000-05-26 | Kawasaki Heavy Ind Ltd | Axial flow blower |
| CN204126915U (en) * | 2014-09-14 | 2015-01-28 | 湖北省风机厂有限公司 | A kind of high thrust reversible tunnel jet blower |
| CN109826802A (en) * | 2019-03-25 | 2019-05-31 | 扬州大学 | A kind of Double-way axial flow pump installation with hiding rear guide vane structure |
| CN210509605U (en) * | 2019-08-27 | 2020-05-12 | 江苏振华泵业制造有限公司 | Angular direct-connected bidirectional axial-flow pump |
| CN112682315A (en) * | 2020-12-17 | 2021-04-20 | 武汉船用电力推进装置研究所（中国船舶重工集团公司第七一二研究所） | Bidirectional axial flow pump |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8736096B2 (en) | Water flow electricity generating device | |
| TWI491798B (en) | Submersible power generating plant, driven by a water flow | |
| CN101701565B (en) | Floating impeller serial hydraulic turbine | |
| CN101578448A (en) | Tidal electricity generating apparatus | |
| CN202550800U (en) | Vortex tube motor | |
| CN102684391A (en) | Vortex tube motor | |
| CN116608131A (en) | Marine bidirectional transverse inclination adjusting pump | |
| CN109538764A (en) | A kind of miniature self-service ship driving shafting grease seal leak-proof device | |
| CN211039055U (en) | Silicon carbide slurry pump | |
| CN210240027U (en) | Planetary gear speed reduction submersible electric pump | |
| CN209430766U (en) | A kind of miniature self-service ship driving shafting grease seal leak-proof device | |
| CN112628146A (en) | Multistage double suction pump with vertical structure | |
| CN112829911A (en) | Counter-rotating rim propeller and underwater traveling tool adopting same | |
| CN215256824U (en) | Horizontal ceramic seawater circulating pump | |
| CN218717664U (en) | Bearing box for dredging | |
| CN217396773U (en) | Novel high-sinking-resistance ship structure | |
| CN110834709A (en) | 360-degree full-rotation inboard and outboard double-motor contra-rotating propeller propelling device overall structure type | |
| CN219673919U (en) | Hydraulic motor special for deepwater operation | |
| CN220452226U (en) | Semi-submersible vertical centrifugal pump | |
| CN219587783U (en) | Vortex type vertical axial flow pump | |
| CN214887623U (en) | Winch disc and pump shaft connecting structure of cutter suction dredger | |
| CN213229099U (en) | 360-degree full-rotation inboard and outboard double-motor contra-rotating propeller propelling device overall structure type | |
| CN215543102U (en) | Hydraulic motor driven large plane cleaner | |
| CN218235515U (en) | Centrifugal pump capable of preventing cavitation phenomenon | |
| CN114439770B (en) | Compact marine water cannon booster centrifugal pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |