WO2023142189A1 - 轴承润滑结构及具有其的筒袋泵 - Google Patents

轴承润滑结构及具有其的筒袋泵 Download PDF

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Publication number
WO2023142189A1
WO2023142189A1 PCT/CN2022/076782 CN2022076782W WO2023142189A1 WO 2023142189 A1 WO2023142189 A1 WO 2023142189A1 CN 2022076782 W CN2022076782 W CN 2022076782W WO 2023142189 A1 WO2023142189 A1 WO 2023142189A1
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Prior art keywords
oil
bearing
main shaft
shaft sleeve
lubricating structure
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PCT/CN2022/076782
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English (en)
French (fr)
Inventor
周维坚
余梦琪
余敏
缪杰
张丹艺
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浙江水泵总厂有限公司
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Application filed by 浙江水泵总厂有限公司 filed Critical 浙江水泵总厂有限公司
Publication of WO2023142189A1 publication Critical patent/WO2023142189A1/zh

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    • 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
    • F04D29/049—Roller 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

Definitions

  • the present application relates to the technical field related to water pumps, in particular to a bearing lubricating structure and a barrel pump having the same.
  • the liquid level of the lubricating oil is usually located at the center of the lower row of balls in a static state, so that after the main shaft starts to rotate, the liquid level of the lubricating oil is at the center of the lower row of balls. Under the action, it is pulled upwards to the center position of the upper row of balls, so as to realize the simultaneous lubrication of the duplex bearings;
  • the present application firstly provides a bearing lubrication structure for barrel pumps, including an oil tank, a main shaft and a bearing assembly, the main shaft runs through the oil tank; the bearing assembly includes a shaft sleeve and a double bearing, and the shaft sleeve is located on the
  • the oil tank is fixed on the main shaft, the inner ring of the duplex bearing is fixed on the shaft sleeve, and the outer ring is relatively fixed to the oil tank, so as to divide the inside of the oil tank into an upper space and a lower space;
  • the bottom end of the bushing is located in the lower space to draw the lubricating oil upward when rotating; the oil tank is also provided with an oil return passage connecting the upper space and the lower space.
  • the lubricating oil can be pulled upward through the shaft sleeve, and the amount of oil transported upwards It is relatively controllable, so that the amount of oil delivered upward can be reduced as much as possible under the premise of meeting the lubrication requirements of the duplex bearing, so as to avoid leakage caused by a large amount of oil flushing the gland, or leakage caused by oil retention.
  • the bottom end of the sleeve has a chamfer inclined from bottom to top in a direction away from the main shaft.
  • the lubricating oil can be thrown out to the lower row of balls of the duplex bearing along the chamfer under the action of centrifugal force, so as to meet the lubrication requirements and reduce the amount of oil transported upwards in the working state, thereby avoiding The effect of oil leakage.
  • the direction of inclination of the chamfer is towards the lower row of balls of the duplex bearing.
  • a plurality of oil suction grooves are provided on the outer peripheral surface of the shaft sleeve, the upper ends of the oil suction grooves communicate with the upper space, and the lower ends communicate with the lower space.
  • two oil suction grooves are symmetrically formed on the outer peripheral surface of the sleeve centering on the central axis of the main shaft.
  • the oil suction groove is in the shape of a helix.
  • the sleeve is provided with a plurality of oil return holes inclined from bottom to top in a direction away from the main shaft, and the oil return holes communicate with the oil suction groove.
  • the lubricating oil between the shaft sleeve and the main shaft can return to the oil suction groove along the oil return hole under the action of centrifugal force.
  • the bottom end of the fuel tank is further provided with a sealing retainer, and the outer side of the sealing retainer is fixedly connected with the fuel tank.
  • the sealing retaining sleeve can prevent the lubricating oil in the oil tank from leaking along the main shaft and through the oil tank, thereby reducing the possibility of oil leakage.
  • part of the sealing retainer is located between the main shaft and the shaft sleeve, and the top end of the sealing retainer corresponds to the inner opening of the oil return hole.
  • the second aspect of the present application provides a barrel pump, which includes the above-mentioned bearing lubricating structure.
  • Fig. 1 is a schematic cross-sectional structure schematic diagram of the front view direction of the bearing frame part of the canister pump in one embodiment of the present application.
  • FIG. 2 is a schematic diagram of an enlarged structure at point A in FIG. 1 .
  • FIG. 3 is an enlarged structural schematic diagram of the shaft sleeve in FIG. 2 .
  • FIG. 4 is a schematic cross-sectional structural diagram of a bearing lubricating structure in a front view direction in another embodiment of the present application.
  • FIG. 5 is a schematic top view of the structure of FIG. 3 .
  • Fig. 6 is a schematic cross-sectional structural diagram of a shaft sleeve in a front view direction in another embodiment of the present application.
  • first and second are used for descriptive purposes only, and cannot be interpreted as indicating or implying relative importance or implicitly specifying the quantity of indicated technical features.
  • the features defined as “first” and “second” may explicitly or implicitly include at least one of these features.
  • “plurality” means at least two, such as two, three, etc., unless otherwise specifically defined.
  • a first feature is “on” or “under” a second feature, which means that the first feature is directly in contact with the second feature, or that the first feature and the second feature are indirectly in contact with each other. contact through an intermediary.
  • “above”, “above” and “above” the first feature on the second feature may mean that the first feature is directly above or obliquely above the second feature, or it just means that the first feature is higher in level than the second feature.
  • “Below”, “beneath” and “under” the first feature may mean that the first feature is directly below or obliquely below the second feature, or it just means that the level of the first feature is smaller than that of the second feature.
  • the present application firstly provides a kind of bearing lubricating structure, is used for barrel pump, comprises oil tank 10, main shaft 20 and bearing assembly 30, and main shaft 20 runs through oil tank 10;
  • Bearing assembly 30 includes shaft sleeve 31 and double The joint bearing 32, the shaft sleeve 31 is located in the oil tank 10 and fixed on the main shaft 20, the inner ring of the double bearing 32 is fixed on the shaft sleeve 31, and the outer ring is relatively fixed to the oil tank 10, so as to divide the inside of the oil tank 10 into an upper space 11 and the lower space 12; the bottom end of the bushing 31 is located in the lower space 12 to draw the lubricating oil upward during rotation;
  • the main shaft 20 After the main shaft 20 starts to rotate, it will drive the shaft sleeve 31 to rotate together, so that the high-speed rotation of the shaft sleeve 31 can pull the lubricating oil upward. Therefore, the lubricating oil liquid level in the oil tank 10 only needs to be at the bottom of the shaft sleeve 31 Just between the double bearing 32, that is, the bottom end of the shaft sleeve 31 is below the lubricating oil level, and the duplex bearing 32 is above the lubricating oil level, so that the oil level in the static state is reduced.
  • the shaft sleeve 31 pulls the lubricating oil upwards, which can be to directly draw the lubricating oil in the lower space 12 to the upper space 11, or to throw the lubricating oil in the lower space 12 to the lower row of balls of the duplex bearing 32, and pass through the lower space.
  • the upward traction force generated when the row of balls rotate further transports the oil upward; the application does not make specific limitations here, as long as the rotation of the shaft sleeve 31 can finally pull the lubricating oil in the lower space 12 upward to the upper space 11, it has The lubrication requirement of a full set of duplex bearings 32 is sufficient.
  • the lubricating oil liquid level in the oil tank 10 in the present application is between the bottom end of the shaft sleeve 31 and the duplex bearing 32, the lower balls of the duplex bearing 32 are not directly immersed in the oil, so after the water pump starts to work, the upward
  • the amount of oil transported is more controllable, for example:
  • the bushing 31 directly draws the lubricating oil in the lower space 12 to the upper space 11, by designing the shape and size of the bottom end of the bushing 31 and the diameter of the traction oil path of the bushing 31, the oil that is delivered upward can be volume adjustment;
  • the shaft sleeve 31 throws the lubricating oil in the lower space 12 to the lower row of balls of the duplex bearing 32, by designing the shape and size of the bottom end of the shaft sleeve 31, the amount of oil liquid thrown to the lower row of balls can be adjusted when it rotates. Further, the amount of oil that the bearing assembly 30 feeds upwards as a whole is adjusted.
  • the amount of oil delivered upwards via the bearing assembly 30 is relatively small on the premise that it can meet the lubrication requirements of the duplex bearing 32, and will not cause leakage due to a large amount of flushing of the oil tank gland; in addition, due to the amount of oil Less, the lubricating oil delivered to the upper space 11 can immediately flow back to the lower space 12 through the oil return passage 13, and is always in a circulating state, and will not cause leakage due to stagnation at the oil tank gland.
  • the oil tank 10 includes a box body 110, a bearing box 120 and a gland 130, wherein the bearing box 120 is located between the box body 110 and the gland 130, and the flange parts of the bearing box 120 are respectively It is fixedly connected with the box body 110 and the gland 130, and the outer ring of the duplex bearing 32 is fixed with the bearing housing 120, so that the outer ring of the duplex bearing 32 is relatively fixed with the oil tank 10, and the duplex bearing 32 cooperates with the bearing housing 120 to
  • the inner space formed by the box body 110 and the gland 130 is divided into two parts: an upper space 11 and a lower space 12;
  • the bottom of the bearing housing 120 is provided with a through hole, so that lubricating oil can enter the bearing housing 120 through the through hole and lubricate the duplex bearing 32; To ensure that the highest point of the circulating oil is lower than the contact surface between the gland 130 and the bearing housing 120, thereby further reducing the possibility of lubricating oil leakage.
  • the bottom end of the shaft sleeve 31 has a chamfer inclined from bottom to top to the direction away from the main shaft 20; so that after the main shaft 20 drives the shaft sleeve 31 to start rotating, the lubricating oil can The lower row of balls thrown out to the double bearing 32 along the chamfer, and transported to the upper space 11 via the double bearing 32, thereby completing the lubrication of the double bearing 32;
  • the bottom end of the bushing 31 can also be other commonly used guide structures, such as inclined guide holes, etc., as long as the lubricating oil can be transported in a designated direction during rotation.
  • the inclination direction of the chamfer is towards the lower row of balls of the duplex bearing 32, so that a large proportion of the oil thrown out through the bushing 31 can be directly thrown to the lower row of balls, and transported upwards through the lower row of balls , to increase the delivery efficiency of lubricating oil.
  • the outer edge surface of axle sleeve 31 is provided with a plurality of oil suction grooves 311, and the upper end of oil suction groove 311 communicates with upper space 11, and the lower end communicates with lower space 12; So that main shaft 20 After the shaft sleeve 31 is driven to rotate, the oil can be transported upward along the oil suction groove 311 to the upper space 11 under the action of the upward traction generated by the rotation of the shaft sleeve 31;
  • the lubricating oil After being transported to the upper space 11, the lubricating oil can flow back to the lower space 12 along the path of the upper row of balls and the lower row of balls under the action of its own weight, and realize the lubrication of the double bearing 32.
  • the excess lubricating oil in the upper space 11 can pass through the return
  • the oil passage 13 returns to the lower space 12 .
  • the upward delivery of lubricating oil depends on the rotation of the shaft sleeve 31, so it is relatively controllable. Specifically, it can be achieved by designing the shape and size of the bottom end of the shaft sleeve 31 and the diameter of the traction oil passage of the shaft sleeve 31. The amount of oil transported upwards is adjusted, so that the amount of oil transported upwards can be reduced while meeting the lubrication requirements, so as to avoid the leakage of lubricating oil.
  • an inner spacer 321 and an outer spacer 322 are fixed between the upper and lower sets of bearings of the duplex bearing 32 , and the inner spacer 321 and the outer spacer 322 are both radially penetrated.
  • There are a plurality of through holes the top of the oil suction groove 311 corresponds to the through hole of the inner spacer 321 , and the oil tank 10 is also provided with an auxiliary oil return passage 15 connecting the upper space 11 and the through hole of the outer spacer 322 .
  • Part of the oil in the upper space 11 can flow back to between the upper and lower sets of bearings through the auxiliary oil return passage 15 and the through hole of the outer spacer 322 , while the oil in the oil suction groove 311 can flow back to the center through the through hole of the inner spacer 321 .
  • the amount of oil in the upper space 11 is less at this time, it means that the amount of oil transported upwards in the oil circuit is less at this time, and the pressure of the oil in the upper space 11 on the upper row of balls is relatively small. It has little or even no influence on the upward traction of the upper row of balls, so the oil located between the two sets of bearings will be transported upward by the upper row of balls to increase the amount of oil transported upwards, thereby increasing the circulation in the cycle. oil volume;
  • the amount of oil in the upper space 11 is relatively large, which means that the amount of oil transported upwards in the oil circuit circulation is large at this time, and the pressure of the oil in the upper space 11 on the upper row of balls is relatively large. It has a great influence on the upward traction of the upper row of balls, so the oil between the two sets of bearings is difficult to transport upwards, and it will flow back down along the lower row of balls under its own gravity, thereby hindering the upward transportation of the lower row of balls Oil to reduce the amount of oil transported upwards, thereby reducing the amount of oil in the cycle;
  • this part of the oil can change the flow direction adaptively according to the amount of oil in the upper space 11, so as to realize the dynamic balance of the amount of oil in the cycle and avoid Too much or too little oil leads to abnormal operation.
  • two oil suction grooves 311 are symmetrically provided on the outer edge surface of the shaft sleeve 31 centered on the central axis of the main shaft 20; in this case, the amount of oil transported upward through the oil suction grooves 311 is just It can meet the lubrication requirements of the upper and lower rows of balls in the double bearing 32, and the oil can form a smooth circulation, and will not stay at the contact surface between the gland 130 and the bearing housing 120, so as to avoid leakage of lubricating oil.
  • the oil suction groove 311 is in the shape of a helix; so that the oil in the oil suction groove 311 can be transported upwards relatively smoothly under the action of the traction force generated by the rotation of the shaft sleeve 31 , which can be applied to parts due to the main shaft 20
  • the rotation speed is relatively low, or the distance between the upper space 11 and the lower space 12 is too large, so that the traction force generated when the shaft sleeve 31 rotates is not enough to transport the oil vertically upward along the oil suction groove 311 .
  • the shaft sleeve 31 is provided with a plurality of oil return holes 312 inclined from bottom to top in the direction away from the main shaft 20, and the oil return holes 312 communicate with the oil suction groove 311;
  • the lubricating oil between the shaft sleeve 31 and the main shaft 20 can return to the oil suction groove 311 along the oil return hole 312 under the action of centrifugal force.
  • the bottom end of the oil tank 10 is also provided with a sealing retainer 14, and the outer side of the sealing retainer 14 is fixedly connected with the fuel tank 10; Lubricating oil leaks along the main shaft 20 through the oil tank 10 , thereby reducing the possibility of oil leakage.
  • part of the seal retainer 14 is located between the main shaft 20 and the shaft sleeve 31, and the top of the seal retainer 14 corresponds to the inner opening of the oil return hole 312; so that the seal retainer 14 and the main shaft Most of the oil between 20 can be transported upwards under the rotation of the main shaft 20 and returned to the oil suction groove 311 through the oil return hole 312, and a small part of the remaining oil can rely on the sealing effect of the sealing retainer 14 to prevent from The lower side leaks to achieve the effect of increasing the sealing effect of the sealing retainer 14 and further reducing the possibility of oil leakage.
  • the present application also provides a barrel pump.
  • the canister pump includes the above-mentioned bearing lubricating structure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

一种轴承润滑结构及具有其的筒袋泵。该轴承润滑结构，用于筒袋泵，包括油箱(10)、主轴(20)以及轴承组件(30)，主轴(20)贯穿油箱(10)；轴承组件(30)包括轴套(31)以及双联轴承(32)，轴套(31)位于油箱(10)内且固设于主轴(20)，双联轴承(32)的内圈固设于轴套(31)，外圈与油箱(10)相对固定，以将油箱(10)内部分隔为上部空间(11)与下部空间(12)；轴套(31)的底端位于下部空间(12)内，以在转动时将润滑油向上牵引；油箱(10)还开设有连通上部空间(11)与下部空间(12)的回油通路(13)。

Description

轴承润滑结构及具有其的筒袋泵
相关申请
本申请要求2022年1月28日申请的，申请号为202210115054.7，发明名称为“轴承润滑结构及具有其的筒袋泵”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及水泵相关技术领域，特别是涉及一种轴承润滑结构及具有其的筒袋泵。
背景技术
目前的筒袋泵及其他水泵轴，为避免引起附加轴向力，并在两个方向将轴限制在轴向游隙范围内，大多采用成对双联安装的角接触球轴承；考虑到轴承的润滑需要，双联轴承多安装于装有润滑油的油箱内；
此外，为保证双联轴承的上下排滚珠均能够得到润滑，静止状态下，润滑油的液面通常位于下排滚珠的中心位置，以使得主轴开始转动后，润滑油的液面在下排滚珠转动作用下向上牵引至上排滚珠的中心位置，从而实现对双联轴承的同时润滑；
但是由于工作状态下润滑油的液面高度较高，接近油箱压盖位置，大量被上排滚珠甩出的油液冲刷压盖或滞留于压盖，从而导致压盖处容易发生润滑油泄漏。
发明内容
基于此，有必要针对现有技术中轴承油箱内油位较高，导致润滑油容易从压盖处泄漏的问题，提供一种能够保证双联轴承得到充分润滑且油位较低不易泄漏的轴承润滑结构及具有其的筒袋泵。
本申请首先提供一种轴承润滑结构，用于筒袋泵，包括油箱、主轴以及轴承组件，所述主轴贯穿所述油箱；所述轴承组件包括轴套以及双联轴承，所述轴套位于所述油箱内且固设于所述主轴，所述双联轴承的内圈固设于所述轴套，外圈与所述油箱相对固定，以将所述油箱内部分隔为上部空间与下部空间；所述轴套的底端位于所述下部空间内，以在转动时将润滑油向上牵引；所述油箱还开设有连通所述上部空间与所述下部空间的回油通路。
上述轴承润滑结构，通过在主轴与双联轴承之间设置轴套，且将轴套的底端设置于双联轴承以下，使得能够通过轴套将润滑油向上牵引，且向上输送的油液量较为可控，从而能够将向上输送的油液量在满足双联轴承润滑需求的前提下尽可能减少，以避免因大量油液冲刷压盖导致泄漏，或因油液滞留导致泄漏的情况发生。
在其中一个实施例中，所述轴套的底端具有自下往上向远离所述主轴方向倾斜的倒角。
可以理解的是，润滑油能够在离心力作用下沿倒角甩出至双联轴承的下排滚珠，以在满足润滑需求的同时，减少了工作状态下向上运输的油液量，从而达到了避免润滑油泄漏的效果。
在其中一个实施例中，所述倒角的倾斜方向朝向所述双联轴承的下排滚珠。
可以理解的是，经由轴套甩出的油液较大比例能够直接甩至下排滚珠， 并经由下排滚珠向上输送，以增加润滑油油液的输送效率。
在其中一个实施例中，所述轴套的外缘面开设有多个吸油槽，所述吸油槽的上端与所述上部空间连通，下端与所述下部空间连通。
可以理解的是，轴套开始转动后，能够将油液沿吸油槽向上输送至上部空间，且向上运输的油液量易于调节，从而能够在满足润滑需求的同时，减少向上运输的油液量，以达到避免润滑油泄漏的效果。
在其中一个实施例中，所述轴套的外缘面以所述主轴的中轴线为中心，对称开设有两个所述吸油槽。
在其中一个实施例中，所述吸油槽呈螺旋线形。
可以理解的是，能够适用于部分因主轴转速相对较低、或上部空间与下部空间之间间距过大，导致轴套转动时所产生的牵引力不足以将油液沿吸油槽垂直向上输送的情况。
在其中一个实施例中，所述轴套周向贯通开设有多个自下往上向远离所述主轴方向倾斜的回油孔，所述回油孔与所述吸油槽连通。
可以理解的是，轴套与主轴之间的润滑油能够在离心力作用下沿回油孔回到吸油槽内。
在其中一个实施例中，所述油箱底端还设置有密封挡套，所述密封挡套的外侧与所述油箱固定连接。
可以理解的是，密封挡套能够避免油箱内的润滑油油液沿主轴从贯穿油箱处泄漏，进而减小油液泄漏的可能。
在其中一个实施例中，部分所述密封挡套位于所述主轴与所述轴套之间，且所述密封挡套的顶端与所述回油孔的内侧开口对应。
可以理解的是，密封挡套与主轴之间的油液，大部分能够在主轴的转动 作用下，向上输送并通过回油孔甩回至吸油槽，以达到增加密封挡套密封效果的作用，进一步减小油液泄漏的可能。
本申请第二方面提供一种筒袋泵，该筒袋泵包括上述的轴承润滑结构。
附图说明
为了更清楚地说明本申请实施例或传统技术中的技术方案，下面将对实施例或传统技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅是本申请的一些实施例，对于本领域普通技术人员而言，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本申请其中一个实施例中筒袋泵轴承架部分的正视方向剖视结构示意图。
图2为图1中A处的放大结构示意图。
图3为图2中轴套的放大结构示意图。
图4为本申请另一实施例中轴承润滑结构的正视方向剖视结构示意图。
图5为图3的俯视结构示意图。
图6为本申请另一实施例中的轴套的正视方向剖视结构示意图。
附图标记：10、油箱；110、箱体；120、轴承箱；130、压盖；11、上部空间；12、下部空间；13、回油通路；14、密封挡套；15、辅助回油通路；20、主轴；30、轴承组件；31、轴套；311、吸油槽；312、回油孔；32、双联轴承；321、内隔圈；322、外隔圈。
具体实施方式
为使本申请的上述目的、特征和优点能够更加明显易懂，下面结合附图 对本申请的具体实施方式做详细的说明。在下面的描述中阐述了很多具体细节以便于充分理解本申请。但是本申请能够以很多不同于在此描述的其它方式来实施，本领域技术人员可以在不违背本申请内涵的情况下做类似改进，因此本申请不受下面公开的具体实施例的限制。
需要说明的是，当组件被称为“固定于”或“设置于”另一个组件，它可以直接在另一个组件上或者也可以存在居中的组件。当一个组件被认为是“连接”另一个组件，它可以是直接连接到另一个组件或者可能同时存在居中组件。本申请的说明书所使用的术语“垂直的”、“水平的”、“上”、“下”、“左”、“右”以及类似的表述只是为了说明的目的，并不表示是唯一的实施方式。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本申请的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本申请中，除非另有明确的规定和限定，第一特征在第二特征“上”、“下”可以是第一特征直接和第二特征接触，或第一特征和第二特征间接地通过中间媒介接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅表示第一特征水平高度小于第二特征。
除非另有定义，本申请的说明书所使用的所有的技术和科学术语与属于本申请的技术领域的技术人员通常理解的含义相同。在本申请的说明书中所 使用的术语只是为了描述具体的实施方式的目的，不是旨在于限制本申请。本申请的说明书所使用的术语“及/或”包括一个或多个相关的所列项目的任意的和所有的组合。
现有技术中，由于需要保证水泵的运行功率，水泵主轴的转速较高且无法随意调节，而高速转动的主轴会带动双联轴承的滚珠高速转动，又由于双联轴承的下排滚珠浸没于油液中，因此高速转动的下排滚珠所产生的向上的牵引力会将大量润滑油向上输送，从而导致经上排滚珠输送至双联轴承上侧的油液量也较大，而在大量油液的冲刷下，油箱压盖处极易发生油液泄漏；
此外由于油液量较大，若回油速度较小，则油液同样容易滞留于油箱压盖处，进而导致油液泄漏，若增大回油管路的管径，虽然能够增加回油速度避免油液滞留的情况发生，但势必会增加装置整体体积，不利于部分较小体积水泵的设计。
请参阅图1至图2，本申请首先提供一种轴承润滑结构，用于筒袋泵，包括油箱10、主轴20以及轴承组件30，主轴20贯穿油箱10；轴承组件30包括轴套31以及双联轴承32，轴套31位于油箱10内且固设于主轴20，双联轴承32的内圈固设于轴套31，外圈与油箱10相对固定，以将油箱10内部分隔为上部空间11与下部空间12；轴套31的底端位于下部空间12内，以在转动时将润滑油向上牵引；油箱10还开设有连通上部空间11与下部空间12的回油通路13。
由于主轴20开始转动后，会带动轴套31一同转动，从而通过轴套31的高速转动，能够将润滑油向上牵引，因此，油箱10内的润滑油液面仅需要位于轴套31的底端与双联轴承32之间即可，即轴套31的底端位于润滑油液面以下，而双联轴承32位于润滑油液面以上，以使得静止状态下的油位高度 降低。
而轴套31将润滑油向上牵引，可以为直接将下部空间12的润滑油牵引至上部空间11，也可以为将下部空间12的润滑油甩至双联轴承32的下排滚珠，并通过下排滚珠转动时产生的向上的牵引力将油液进一步向上输送；本申请在此不做具体限定，只要通过轴套31的转动，最终能够将下部空间12的润滑油向上牵引至上部空间11，已满组双联轴承32的润滑需求即可。
当润滑油液被牵引至上部空间11后，能够沿回油通路13回流至下部空间12，以避免润滑油液在上部空间11内滞留，从而导致油箱压盖处发生油液泄漏。
由于本申请中油箱10内的润滑油液面位于轴套31的底端与双联轴承32之间，双联轴承32的下排滚珠未直接浸没于油液中，因此水泵开始工作后，向上运输的油液量较为可控，例如：
在轴套31直接将下部空间12的润滑油牵引至上部空间11的情况下，通过设计轴套31底端的形状、大小以及轴套31牵引油路的管径均可对向上输油的油液量进行调节；
在轴套31将下部空间12的润滑油甩至双联轴承32的下排滚珠的情况下，通过设计轴套31底端的形状、大小能够调节其转动时甩至下排滚珠的油液量，进而调节轴承组件30整体向上输油的油液量。
因此本申请中，经由轴承组件30向上输送的油液量，在能够满足双联轴承32润滑需求的前提下相对较少，不会因大量冲刷油箱压盖从而导致泄漏；此外，由于油液量较少，输送至上部空间11的润滑油能够通过回油通路13立即回流至下部空间12，并始终处于一循环状态，不会因滞留于油箱压盖处而导致泄漏。
在图2所示的实施例中，油箱10包括箱体110、轴承箱120以及压盖130，其中，轴承箱120位于箱体110与压盖130之间，且轴承箱120的法兰部分别与箱体110与压盖130固定连接，双联轴承32的外圈与轴承箱120固定，以使得双联轴承32的外圈与油箱10相对固定，并且双联轴承32与轴承箱120配合将箱体110与压盖130所形成的内部空间分隔为上部空间11与下部空间12两个部分；
轴承箱120的底端开设有通孔，以使得润滑油能够通过该通孔进入轴承箱120内并对双联轴承32进行润滑；双联轴承32的顶端位于压盖130与轴承箱120的接触面以下，以保证循环油液的最高点低于压盖130与轴承箱120的接触面，从而能够进一步减小润滑油泄漏的可能。
在图2所示的实施例中，轴套31的底端具有自下往上向远离主轴20方向倾斜的倒角；以使得在主轴20带动轴套31开始转动后，润滑油能够在离心力作用下沿倒角甩出至双联轴承32的下排滚珠，并经由双联轴承32牵引输送至上部空间11，从而完成对双联轴承32的润滑；
以使得在初始油位降低的情况下也能够实现油液的向上输送；并且将倒角甩出润滑油油液的过程作为中介，在满足润滑需求的同时，减少了工作状态下向上运输的油液量，从而达到了避免润滑油泄漏的效果。
当然，轴套31的底端也可以为其他常用的导向结构，如贯通开设有倾斜的导向孔等，只要能够在转动时将润滑油油液向指定方向输送即可。
在上述实施例中，倒角的倾斜方向朝向双联轴承32的下排滚珠，以使得经由轴套31甩出的油液较大比例能够直接甩至下排滚珠，并经由下排滚珠向上输送，以增加润滑油油液的输送效率。
在图2和图3所示的实施例中，轴套31的外缘面开设有多个吸油槽311， 吸油槽311的上端与上部空间11连通，下端与下部空间12连通；以使得主轴20带动轴套31开始转动后，油液能够轴套31转动产生的向上的牵引力的作用下，沿吸油槽311向上输送至上部空间11；
输送至上部空间11后，润滑油能够自重作用下，沿上排滚珠、下排滚珠的路径回流至下部空间12，并实现对双联轴承32的润滑，上部空间11多余的润滑油能够通过回油通路13回流至下部空间12。
在上述实施例中，润滑油的向上输送依靠轴套31的转动实现，因此较为可控，具体的，通过设计轴套31底端的形状、大小以及轴套31牵引油路的管径等均可对向上运输的油液量进行调节，从而能够在满足润滑需求的同时，减少向上运输的油液量，以达到避免润滑油泄漏的效果。
在图4所示的实施例中，双联轴承32的上下两组轴承之间固设有内隔圈321与外隔圈322，且内隔圈321与外隔圈322均沿径向贯通开设有多个通孔，吸油槽311的顶端与内隔圈321的通孔对应，油箱10还开设有连通上部空间11与外隔圈322的通孔的辅助回油通路15。
上部空间11的部分油液能够通过辅助回油通路15以及外隔圈322的通孔回流至上下两组轴承之间，而吸油槽311内的油液能够通过内隔圈321的通孔回流至上下两组轴承之间；
若此时上部空间11内的油液量较少，即代表此时油路循环内向上输送的油液量较少，且此时上部空间11内的油液对上排滚珠的压力较小，对上排滚珠转动向上牵引油液的影响较小甚至没有影响，因此位于两组轴承之间的油液会被上排滚珠牵引向上运输，以增加向上运输的油液量，进而增加循环内的油液量；
而此时上部空间11内的油液量较多，即代表此时油路循环内向上输送的 油液量较多，且此时上部空间11内的油液对上排滚珠的压力较大，对上排滚珠向上牵引油液的影响较大，因此两组轴承之间的油液较难进一步向上运输，并且会在自身重力作用下沿下排滚珠向下回流，进而阻碍下排滚珠向上运输油液，以减少向上运输的油液量，进而减少循环内的油液量；
因此，通过将油液引入两组轴承之间，该部分油液能够根据上部空间11内的油液量自适应的改变流向，以实现对循环内油液量的动态平衡，避免因循环内的油液量过多或过少导致运行异常的情况发生。
在图5所示的实施例中，轴套31的外缘面以主轴20的中轴线为中心，对称开设有两个吸油槽311；此情况下，通过吸油槽311向上运输的油液量恰好能够满足双联轴承32上下排滚珠的润滑需求，且油液能够形成通畅的循环，不会在压盖130与轴承箱120的接触面处滞留，以达到避免润滑油泄漏的效果。
在图6所示的实施例中，吸油槽311呈螺旋线形；使得吸油槽311内油液能够在轴套31转动所产生的牵引力作用下，较为平滑的向上输送，能够适用于部分因主轴20转速相对较低、或上部空间11与下部空间12之间间距过大，导致轴套31转动时所产生的牵引力不足以将油液沿吸油槽311垂直向上输送的情况。
在图2和图3所示的实施例中，轴套31周向贯通开设有多个自下往上向远离主轴20方向倾斜的回油孔312，回油孔312与吸油槽311连通；以使得轴套31与主轴20之间的润滑油能够在离心力作用下沿回油孔312回到吸油槽311内。
在图2所示的实施例中，油箱10底端还设置有密封挡套14，密封挡套14的外侧与油箱10固定连接；密封挡套14通过迷宫密封的原理，以避免油 箱10内的润滑油油液沿主轴20从贯穿油箱10处泄漏，进而减小油液泄漏的可能。
在图2所示的实施例中，部分密封挡套14位于主轴20与轴套31之间，且密封挡套14的顶端与回油孔312的内侧开口对应；以使得密封挡套14与主轴20之间的油液，大部分能够在主轴20的转动作用下，向上输送并通过回油孔312甩回至吸油槽311，小部分残留油液则能够依靠密封挡套14的密封作用防止从下侧泄漏，以达到增加密封挡套14密封效果的作用，进一步减小油液泄漏的可能。
本申请还提供一种筒袋泵。该筒袋泵包括上述的轴承润滑结构。
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对申请专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请的专利保护范围应以所附权利要求为准。

Claims (10)

  1. 一种轴承润滑结构，用于筒袋泵，其特征在于，包括油箱、主轴以及轴承组件，所述主轴贯穿所述油箱；
    所述轴承组件包括轴套以及双联轴承，所述轴套位于所述油箱内且固设于所述主轴，所述双联轴承的内圈固设于所述轴套，外圈与所述油箱相对固定，以将所述油箱内部分隔为上部空间与下部空间；
    所述轴套的底端位于所述下部空间内，以在转动时将润滑油向上牵引；
    所述油箱还开设有连通所述上部空间与所述下部空间的回油通路。
  2. 根据权利要求1所述的轴承润滑结构，其中，所述轴套的底端具有自下往上向远离所述主轴方向倾斜的倒角。
  3. 根据权利要求2所述的轴承润滑结构，其中，所述倒角的倾斜方向朝向所述双联轴承的下排滚珠。
  4. 根据权利要求1所述的轴承润滑结构，其中，所述轴套的外缘面开设有多个吸油槽，所述多个吸油槽的上端与所述上部空间连通，下端与所述下部空间连通。
  5. 根据权利要求4所述的轴承润滑结构，其中，所述轴套的外缘面以所述主轴的中轴线为中心，对称开设有两个所述吸油槽。
  6. 根据权利要求4所述的轴承润滑结构，其中，所述吸油槽呈螺旋线形。
  7. 根据权利要求4所述的轴承润滑结构，其中，所述轴套周向贯通开设有多个自下往上向远离所述主轴方向倾斜的回油孔，所述多个回油孔与所述多个吸油槽连通。
  8. 根据权利要求7所述的轴承润滑结构，其中，所述油箱底端还设置有密封挡套，所述密封挡套的外侧与所述油箱固定连接。
  9. 根据权利要求8所述的轴承润滑结构，其中，部分所述密封挡套位于所述主轴与所述轴套之间，且所述密封挡套的顶端与所述回油孔的内侧开口对应。
  10. 一种筒袋泵，其特征在于，包括如权利要求1-9中任意一项所述的轴承润滑结构。
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