Condensate pump with double oil seal

Abstract

The utility model belongs to sealing element technical field discloses a condensate pump with double -layer oil seal, including the bearing chamber end cover of pump body installation, the bearing chamber end cover is equipped with first oil seal groove, first oil seal groove is installed with first oil seal ring, bearing chamber end cover upper side is installed with oil seal tray, oil seal tray is equipped with second oil seal groove, second oil seal groove is installed with second oil seal ring, oil seal tray upper side is installed with oil seal gland, adopt the structure design of the utility model, the design of double -layer oil seal can effectively solve the bearing chamber from oil seal place oil leakage problem, the maximum degree limit external impurity enters into the bearing chamber, the middle chamber formed by double -layer structure can balance the pressure difference of oil baffle both sides, relieve pressure impact to the influence of sealing, reduce the sudden leakage due to the sudden change of working condition, reduce the heat generation of friction when the shaft rotates, reduce the wear rate of oil seal and journal, adapt long -term high -speed operation demand.

Description

Technical Field

[0001] This utility model belongs to the field of sealing technology, specifically relating to a condensate pump with a double-layer oil seal. Background Technology

[0002] Condensate pumps are key equipment in thermal power generation systems used to transport condensate from condensers. They are typically cylindrical, bag-type, vertical, multi-stage centrifugal pumps. The bearing housing consists of radial sliding bearings and axial thrust sliding bearings. The seal between the moving and stationary parts of the bearing housing and the outside is achieved by two halves of graphite wear-resistant rings, elastically fixed with springs, which work in conjunction with the thrust head to provide a seal. However, during prolonged operation, wear can easily occur at the contact points between the graphite wear-resistant rings and the moving and stationary parts of the thrust head, causing grooves to appear on the thrust head. During rotor rotation, the shaft and thrust disc agitate the lubricating oil, creating an upward deflection. This can easily cause lubricating oil to be flung out through the wear gaps in the oil seal teeth along the thrust head, resulting in oil leakage.

[0003] The shortcomings of existing oil seal technology: Traditional condensate pump oil baffle structures are simple, and even with copper tooth labyrinth seals, the sealing efficiency is poor. Long-term operation causes wear on the labyrinth oil baffle teeth, severely reducing the oil baffle's sealing performance and ultimately leading to lubricating oil leakage. Furthermore, if the original floating oil baffle is replaced with a contact seal, and a frameless oil seal is installed on the shaft below the oil baffle in the oil tank, the frameless oil seal cannot be fixed in place due to the smooth surface of the shaft and the lack of a fixed point. After the rotor rotates for a period of time, the frameless oil seal will be thrown onto the bearing cover, failing to function as an oil baffle.

[0004] Oil leakage in the bearing chamber of a condensate pump can cause the oil level to drop rapidly. When the oil level is insufficient, the thrust bearing of the condensate pump can easily burn out. Due to gaps in the sealing position, dust can easily enter the bearing chamber and cause grease contamination. Utility Model Content

[0005] In view of the problems mentioned above in the background art, the purpose of this utility model is to provide a condensate pump with a double-layer oil seal.

[0006] To achieve the above-mentioned technical objectives, the technical solution adopted by this utility model is as follows: A condensate pump with a double-layer oil seal includes a bearing chamber end cover mounted on the pump body. The bearing chamber end cover has a first oil seal groove and a first oil seal ring installed in the first oil seal groove. An oil seal disc is installed on the upper side of the bearing chamber end cover. The oil seal disc has a second oil seal groove and a second oil seal ring installed in the second oil seal groove. An oil seal gland is installed on the upper side of the oil seal disc.

[0007] Furthermore, the oil seal disc includes two identical semicircular discs, a first semicircular disc and a second semicircular disc. The first semicircular disc has a first protrusion and a first groove, and the second semicircular disc has a second protrusion and a second groove. The position and dimensions of the second protrusion are adapted to the first groove, and the position and dimensions of the second groove are adapted to the first protrusion. This design, with its separate structure, allows for installation without completely disassembling the upper and lower components, making it more convenient and faster. Moreover, the cooperation between the protrusion and the groove improves the stability and accuracy of the installation.

[0008] Further defined, the first semi-circular disk is provided with a first through hole and a first threaded hole, and the second semi-circular disk is provided with a second through hole and a second threaded hole. The position and size of the second through hole correspond to the first threaded hole, and the position and size of the second threaded hole correspond to the first threaded hole. Both the first threaded hole and the second threaded hole are adapted to be installed with locking screws. With this design, the connection and fixation between the first semi-circular disk and the second semi-circular disk can be achieved by using locking screws. Subsequent disassembly is also convenient and quick, and it is easy to repair and replace.

[0009] Furthermore, the contact surfaces between the oil seal disc and the bearing housing end cover are coated with sealant, a design that enhances the sealing performance between the two.

[0010] Further specified, the inner diameter of the oil seal disc is 190mm, the outer diameter is 320mm, the thickness is 30mm, and it is provided with 6 M6 screw holes for connection. The diameter of the second oil seal groove is 250mm and the groove depth is 0.5mm. This design ensures the fit effect.

[0011] The beneficial effects of using this utility model are as follows: By adopting the structural design of this utility model, the oil sealing effect of the first oil sealing groove is enhanced under the effect of the oil sealing disc, and the second oil sealing groove installed on it further enhances the oil sealing effect. Under the effect of double oil sealing, the oil leakage problem is effectively prevented. The double-layer oil seal design can effectively solve the problem of oil leakage from the bearing chamber at the oil seal, and limit the entry of external impurities into the bearing chamber to the greatest extent. The intermediate chamber formed by the double-layer structure can balance the pressure difference on both sides of the oil baffle (such as internal oil pressure fluctuations and external water vapor pressure), alleviate the impact of pressure shock on the seal, and reduce sudden leakage caused by sudden changes in operating conditions. The double-layer spacing design reduces frictional heat generation during shaft rotation, lowers the wear rate of oil seals and journals, and meets the requirements of long-term high-speed operation; The separate oil seal disc has a simple structure that is easy to install and does not increase the difficulty of construction. Its good sealing effect reduces the loss of lubricating oil, reduces the frequency of oil replenishment, and reduces environmental pollution and equipment cleaning costs caused by oil leakage. Attached Figure Description

[0012] This utility model can be further illustrated by the non-limiting embodiments given in the accompanying drawings; Figure 1 This is a schematic diagram of the structure of a condensate pump with a double-layer oil seal according to the present invention; Figure 2 This is a structural schematic diagram of the bearing chamber end cover position of an embodiment of a condensate pump with a double-layer oil seal according to this utility model; Figure 3 for Figure 2 A schematic diagram of the exploded structure; Figure 4 This is a schematic diagram of the oil seal disc structure of an embodiment of a condensate pump with a double-layer oil seal according to the present invention; Figure 5 This is a schematic diagram of the bottom structure of the oil seal plate of an embodiment of a condensate pump with a double-layer oil seal according to the present invention; The symbols for the main components are explained below: 1. Bearing housing end cover; 2. First oil seal groove; 3. First oil seal ring; 4. Oil seal disc; 5. Second oil seal groove; 6. Second oil seal ring; 7. Oil seal gland; First semi-circular disk 41; second semi-circular disk 42; first protrusion 43; first groove 44; second protrusion 45; second groove 46; first through hole 47; first threaded hole 48; second through hole 49; second threaded hole 410; locking screw 411. Detailed Implementation

[0013] To enable those skilled in the art to better understand this utility model, the technical solution of this utility model will be further described below in conjunction with the accompanying drawings and embodiments. Example

[0014] like Figures 1-5 As shown, the present invention discloses a condensate pump with a double-layer oil seal, including a bearing chamber end cover 1 installed on the pump body, the bearing chamber end cover 1 having a first oil seal groove 2, the first oil seal groove 2 having a first oil seal ring 3 installed thereon, an oil seal disc 4 installed on the upper side of the bearing chamber end cover 1, the oil seal disc 4 having a second oil seal groove 5, the second oil seal groove 5 having a second oil seal ring 6 installed thereon, and an oil seal pressure cover 7 installed on the upper side of the oil seal disc 4.

[0015] In this implementation case, the first oil seal ring 3 is first directly installed into the first oil seal groove 2 of the bearing housing end cover 1. This is the first layer of oil seal, which is also a common oil seal measure. On this basis, the oil seal disc 4 is installed above the first oil seal groove 2. The installation of the oil seal disc 4 presses down the first oil seal ring 3. At the same time, the second oil seal ring 6 is installed in the second oil seal groove 5 above it, thus forming a double layer of seal. The intermediate cavity naturally formed between the first oil seal ring 3 and the second oil seal ring 6 can balance the pressure difference on both sides of the oil baffle, alleviate the impact of pressure shock on the seal, and reduce sudden leakage caused by sudden changes in operating conditions. Finally, the oil seal cover 7 is fastened to the bearing with bolts. The installation of the oil seal cover 7 is a common installation method in the prior art, which is not difficult for those skilled in the art to operate and understand. Example

[0016] like Figure 4 , Figure 5 As shown, the oil seal disk 4 includes two identical semi-circular disks, a first semi-circular disk 41 and a second semi-circular disk 42. The first semi-circular disk 41 is provided with a first protrusion 43 and a first groove 44. The second semi-circular disk 42 is provided with a second protrusion 45 and a second groove 46. The position and size of the second protrusion 45 are adapted to the first groove 44, and the position and size of the second groove 46 are adapted to the first protrusion 43.

[0017] In this implementation case, the oil seal disk 4 adopts a modular split-half design. The core consists of a first semi-circular disk 41 and a second semi-circular disk 42 with completely identical structural parameters. Both are integrally formed by metal stamping or injection molding to ensure that the disk surface flatness error is ≤0.1mm, which is suitable for subsequent sealing requirements. On the splicing end face of the first semi-circular disk 41, there is a set of first protrusions 43 and a set of first grooves 44 symmetrically processed radially. The first protrusions 43 are cuboid structures with a height consistent with the thickness of the semi-circular disk. The first grooves 44 are rectangular grooves that match the first protrusions 43. The groove depth, groove width, and groove length correspond completely to the height, width, and length of the protrusion, respectively. Moreover, the inner wall roughness Ra of the groove is ≤1.6μm to reduce the frictional resistance during splicing. The splicing end face of the second semi-circular disk 42 corresponds to the mirror image of the first semi-circular disk 41; the dimensions are also perfectly matched. When splicing, first align the protrusions in the two semi-circular disks with the grooves of the other disk, apply axial force to make the protrusions fully embedded in the grooves. At this time, the inner and outer rings of the two disks form complete circles respectively, and the splicing gap is ≤0.05mm. Finally, fix to complete the overall assembly. The fixing method includes, but is not limited to, spot welding or bolt connection. There are various connection methods, but it is necessary to ensure the connection strength and the smoothness of the upper and lower surfaces. The split structure allows for the placement of two semi-discs on either side of the shaft part to be sealed before splicing, eliminating the need for a single, integral mounting from the shaft end, unlike integrated oil seals. This is particularly suitable for scenarios where the shaft end is fixed and surrounding components create limited installation space, reducing the need to disassemble surrounding parts and improving installation efficiency by over 40%. Since the first and second semi-discs are structurally identical, only one set of production molds is required for mass production, reducing mold costs compared to creating separate molds for two different semi-discs. Furthermore, inventory management eliminates the need to differentiate between the two types of parts, requiring only a single specification of semi-disc to be stocked, increasing inventory turnover. The ability to flexibly adapt to different batches' assembly needs through on-demand splicing reduces the backlog of slow-moving parts. The "convex-concave fit" of the protrusions and grooves creates mechanical positioning, preventing circumferential offset or radial misalignment during splicing, ensuring a stable fit between the inner ring of the oil seal and the shaft part after splicing, effectively preventing leakage of the sealing medium. Simultaneously, the "interlocking structure" formed by the protrusions embedded in the grooves enhances overall impact resistance, reduces structural deformation under vibration, and extends service life. Example

[0018] like Figure 4 , Figure 5 As shown, the first semicircular disk 41 is provided with a first through hole 47 and a first threaded hole 48, and the second semicircular disk 42 is provided with a second through hole 49 and a second threaded hole 410. The position and size of the second through hole 49 correspond to the first threaded hole 48, and the position and size of the second threaded hole 410 correspond to the first threaded hole 48. Both the first threaded hole 48 and the second threaded hole 410 are fitted with locking screws 411.

[0019] In this embodiment, during splicing, after the protrusions and grooves of the two semi-discs are fitted together, the locking screws 411 are respectively passed through the first through hole 47 and screwed into the second threaded hole 410, and through the second through hole 49 and screwed into the first threaded hole 48, until the screws are fully tightened, thus fixing the two semi-discs. The cross-locking structure of the screws can further enhance the splicing stability, prevent loosening under vibration, and improve the overall structural rigidity. The precise correspondence between the through holes and the threaded holes can quickly locate the screw installation position and simplify the assembly process. After tightening, the splicing gap can be reduced, and the concave-convex structure can further improve the sealing performance and prevent media leakage. Example

[0020] like Figure 2 As shown, sealant is applied to the contact surface between the oil seal plate 4 and the bearing housing end cover 1; In this implementation case, firstly, the oil and impurities on the contact surfaces of both are cleaned to ensure the surfaces are dry and clean. Then, a layer of oil-resistant sealant is evenly applied to the contact surface of the oil seal plate 4 facing the bearing housing end cover 1, along the annular area between the outer and inner rings of the contact surface. This includes, but is not limited to, using silicone or anaerobic sealants. After application, the contact surfaces of the oil seal plate 4 and the bearing housing end cover 1 are precisely fitted together, and then the two are fixed together using bolt assemblies. The sealant is allowed to cure at room temperature to complete the sealing assembly. The sealant can fill the tiny gaps on the contact surfaces, blocking the channels for oil leakage from the contact surfaces. Compared with sealing by simply bonding the metal surfaces together, the sealing performance is improved. The oil-resistant sealant can withstand the oil temperature changes during equipment operation, and is not prone to aging or cracking with long-term use, thus extending the seal failure cycle. The sealant also has a certain buffering effect, which can reduce the impact of equipment vibration on the fit of the contact surfaces of both, avoid the increase of the sealing gap due to vibration, and maintain a stable sealing effect. Example

[0021] like Figure 4 As shown, the inner diameter of the oil seal plate 4 is 190mm, the outer diameter is 320mm, the thickness is 30mm, and it has 6 M6 screw holes for connection. The diameter of the second oil seal groove 5 is 250mm, and the groove depth is 0.5mm.

[0022] In this implementation case, the oil seal plate 4 is precisely sized according to the adaptation requirements: an inner diameter of 190mm to match the outer diameter of the shaft part to be sealed, an outer diameter of 320mm to match the inner diameter of the corresponding mounting cavity, and a thickness of 30mm to ensure structural strength while adapting to the installation space; six M6 screw holes are evenly distributed along the outer ring of the oil seal plate for bolt connection with adjacent components; the second oil seal groove 5 has a diameter of 250mm to match the outer diameter of the seal, and a groove depth of 0.5mm to precisely accommodate the seal, ensuring that the seal can be tightly embedded in the groove. During assembly, the oil seal plate is precisely matched with the shaft and mounting cavity through its inner and outer diameters, and fixed by means of the M6 ​​screw holes; the second oil seal groove, through size adaptation, ensures stable installation of the seal, achieving overall adaptation assembly. The inner diameter, outer diameter, thickness, and screw hole size of the oil seal disc are all set according to the matching standard, which can quickly and accurately connect with the corresponding parts, avoiding assembly difficulties caused by dimensional deviations and improving assembly efficiency. The diameter and depth of the second oil seal groove are adapted to the sealing element, which can ensure that the sealing element fits tightly with the groove wall, enhance the sealing effect, and prevent oil leakage. The standardized size design facilitates mass production and reduces the difficulty of matching parts during subsequent maintenance, thus improving overall practicality.

[0023] The above embodiments are merely illustrative of the principles and effects of this utility model and are not intended to limit the scope of this utility model. Any person skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of this utility model. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in this utility model should still be covered by the claims of this utility model.

Claims

1. A condensate pump with a double-layer oil seal, comprising a bearing chamber end cover (1) mounted on the pump body, the bearing chamber end cover (1) having a first oil seal groove (2), the first oil seal groove (2) being fitted with a first oil seal ring (3), characterized in that: An oil seal plate (4) is installed on the upper side of the bearing chamber end cover (1). The oil seal plate (4) is provided with a second oil seal groove (5). A second oil seal ring (6) is installed in the second oil seal groove (5). An oil seal cover (7) is installed on the upper side of the oil seal plate (4).

2. A condensate pump with a double-layer oil seal according to claim 1, characterized in that: The oil seal disc (4) includes two identical semi-circular discs: a first semi-circular disc (41) and a second semi-circular disc (42). The first semi-circular disc (41) is provided with a first protrusion (43) and a first groove (44). The second semi-circular disc (42) is provided with a second protrusion (45) and a second groove (46). The position and size of the second protrusion (45) are adapted to the first groove (44), and the position and size of the second groove (46) are adapted to the first protrusion (43).

3. A condensate pump with a double-layer oil seal according to claim 2, characterized in that: The first semicircular disk (41) is provided with a first through hole (47) and a first threaded hole (48), and the second semicircular disk (42) is provided with a second through hole (49) and a second threaded hole (410). The position and size of the second through hole (49) correspond to the first threaded hole (48), and the position and size of the second threaded hole (410) correspond to the first threaded hole (48). Both the first threaded hole (48) and the second threaded hole (410) are fitted with locking screws (411).

4. A condensate pump with a double-layer oil seal according to claim 1, characterized in that: The contact surfaces between the oil seal plate (4) and the bearing chamber end cover (1) are coated with sealant.

5. A condensate pump with a double-layer oil seal according to claim 1, characterized in that: The inner diameter of the oil seal plate (4) is 190mm, the outer diameter is 320mm, the thickness is 30mm, and it is provided with 6 M6 screw holes for connection. The diameter of the second oil seal groove (5) is 250mm and the groove depth is 0.5mm.

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