CN114320888A - Helical gear pump and method for eliminating axial force thereof - Google Patents
Helical gear pump and method for eliminating axial force thereof Download PDFInfo
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- CN114320888A CN114320888A CN202111327943.1A CN202111327943A CN114320888A CN 114320888 A CN114320888 A CN 114320888A CN 202111327943 A CN202111327943 A CN 202111327943A CN 114320888 A CN114320888 A CN 114320888A
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Abstract
The invention discloses a helical gear pump and an axial force eliminating method thereof, and the helical gear pump comprises a helical gear pump and is characterized in that the helical gear pump comprises a pump body, a pair of meshed helical gears are arranged in the pump body, both sides of the helical gears are respectively provided with a floating bearing and a fixed bearing, the other end of the floating bearing is also provided with a plurality of compensating springs, an oil well hole is also arranged in the pump body, the compensating springs are limited in the oil well hole, the eccentric installation arrangement of the floating bearing is reduced, the action line of a pressing force is superposed with the action line of a reverse thrust, the axial force offset in a fixed distance is realized, the compensating springs are arranged in the combined arrangement of end faces, a certain pretightening force is generated on the end faces to compensate the axial force generated by meshing of the helical gears, the working efficiency of the pump is effectively improved, and the service life of the pump is effectively prolonged.
Description
Technical Field
The invention relates to the technical field of helical gear pumps, in particular to a method for eliminating axial force of a helical gear.
Background
The traditional oil pump adopts a straight gear pump, and has the defects that the contact line of the straight gear is parallel to the axis, and the gear teeth enter and separate simultaneously during working, so that the problems of large flow pulsation, large vibration impact, high noise and the like of the pump are caused, and the problems are more obvious at high rotating speed; for the helical gear pump, when two helical gears are engaged for transmission, from the engagement, the contact line on the tooth surface of the helical gear is firstly lengthened from short to long, then shortened from long to disengaged, and the process of gradual engagement is a process of gradual engagement, under the same condition, the engagement process of the helical gear is longer than that of the straight gear, so that the load of each pair of gears is reduced, the transmission is more stable, the noise is effectively controlled, the helical gear pump is suitable for high speed and heavy load, and the mechanical efficiency of the product is improved, although the helical gear pump is superior to the straight gear pump in terms of efficiency and application effect, due to the existence of the helical angle of the helical gear, a certain axial force exists in the engagement transmission process, and due to the uneven stress on two sides of the gear shaft, the helical gear pump can form a force which is axially directed to the inlet direction of the driving shaft and simultaneously acts on the gears, and the force makes the whole engagement gear of the pump move to the inlet end of the driving shaft gear, causing vibration of the pump, heating of the bearing and even damaging the machine parts, so that the pump can not work normally.
Disclosure of Invention
The invention mainly aims to provide an oblique gear pump and a method for eliminating axial force thereof, which can effectively solve the problems in the background art.
In order to achieve the purpose, the invention adopts the technical scheme that:
the helical gear pump comprises a pump body, a pair of meshed helical gears is arranged in the pump body, floating bearings and fixed bearings are respectively arranged on two sides of each helical gear, a plurality of compensating springs are arranged at the other ends of the floating bearings, oil well holes are further formed in the pump body and used for positioning and limiting the positions of the springs, and therefore the diameter of each oil well is not smaller than the diameter of each spring.
Preferably, the width-diameter ratio of the bevel gear is 0.2-1.5, the spiral critical angle is 10-30 degrees, the modification amount in the tooth direction is not more than 0.05, the addendum coefficient is 0.05-0.25, the arc radius of the tooth root is about 0.4-0.8 times of the modulus, and the tooth tip is further provided with a chamfer not more than R0.1 in the tooth direction.
Preferably, the method for eliminating the axial force is an arrangement and combination mode of the floating bearing, the oil well hole and the compensation spring, and the arrangement and combination mode comprises an eccentric position of the floating spring, an arrangement mode of the oil well hole, an installation position of the compensation spring and a mutual combination mode of the floating bearing, the oil well hole and the compensation spring.
Preferably, the compensation springs are uniformly distributed on the end face of the floating bearing.
Preferably, the compensation springs are non-uniformly distributed on the end face of the floating bearing.
Preferably, the compensation springs are distributed on the end face of the floating bearing in a staggered mode.
Preferably, the number and the arrangement position of the oil well holes correspond to those of the compensation springs, the oil well holes are respectively arranged on the inner end face of the pump body, and the oil well holes are used for limiting the positions of the compensation springs and uniformly converting the elastic force of the compensation springs into pre-tightening force acting between the inner end face of the pump body and the floating bearing and the gear.
Preferably, the compensation springs are distributed on the end face of the floating bearing in different specifications, namely the compensation springs can be arranged on the end face of the floating bearing in different modes to generate pre-tightening force required for counteracting the axial force generated by meshing of the helical gears.
Preferably, the gear pump is further provided with oil wells of different depths to confine the compensating spring.
Preferably, the floating bearing is eccentrically installed, the eccentric position (X0 and Y0) of the floating bearing is that the value range of X0 is (0.1-2) mm, and the value range of Y0 is (0.2-3.5).
Preferably, the working end face of the floating bearing is further provided with an unloading groove and a pressure equalizing groove, an extended oil suction groove is additionally arranged, and the end face of the floating bearing is further provided with a high-pressure oil passing hole.
Compared with the prior art, the invention has the following beneficial effects:
the utility model provides a helical gear pump and elimination method of axial force thereof, including the helical gear pump, its characterized in that, the helical gear pump is equipped with a pair of helical gear of meshing including the pump body in, the pump body, floating bearing and fixing bearing are still respectively installed to the both sides of helical gear, floating bearing's the other end still is equipped with a plurality of compensation springs, still be equipped with the oil well hole in the pump body, compensation spring is restricted in the oil well hole, reduces axial skew the eccentric installation of floating bearing sets up, makes the line of action of the pressure force coincide with the line of action of the reaction thrust, and the offset axial force on the degree of making one fix a distance, compensation spring locates the combined array of terminal surface for the terminal surface has produced certain pretightning force and is used for compensating the offset helical gear meshing produced axial force.
Drawings
FIG. 1 is a first schematic structural diagram of the present invention;
FIG. 2 is a second schematic structural view of the present invention;
FIG. 3 is a schematic view of a bearing structure of the present invention;
FIG. 4 is a schematic end view of the floating bearing of the present invention;
FIG. 5 is a first schematic diagram of the distribution of compensation springs according to the present invention;
FIG. 6 is a second schematic diagram of the distribution of the compensating springs of the present invention;
FIG. 7 is a third schematic diagram of the distribution of the compensating springs of the present invention;
in the figure: 1-pump body, 11-oil well hole, 2-helical gear, 2A-driving shaft helical gear, 2B-driven shaft helical gear, 3-floating bearing, 31-unloading groove, 32-extended oil suction groove, 33-pressure equalizing groove, 34-high pressure oil leading hole, 3A-driving shaft floating bearing, 3B-driven shaft floating bearing, 4-fixed bearing, 4A-driving shaft fixed bearing, 4B-driven shaft floating bearing and 5-compensating spring.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention; furthermore, unless expressly stated or limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, as they may be fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the embodiment, as shown in fig. 1 and 2, a helical gear pump and a method for eliminating an axial force thereof include a helical gear 2 pump, and are characterized in that the helical gear pump includes a pump body 1, a pair of helical gears 2 engaged with each other is disposed in the pump body 1, floating bearings 3 and fixed bearings 4 are respectively disposed on two sides of the helical gears 2, a plurality of compensation springs 5 are further disposed on the other ends of the floating bearings 3, an oil well hole 11 is further disposed in the pump body 1, one end of each compensation spring 5 is mounted on the floating bearing 3, and the other end of each compensation spring is fixed in the oil well hole 11. The width-diameter ratio range of the helical gear 2 is 0.2-1.5, the spiral critical angle is 10-30 degrees, the tooth direction modification amount is not more than 0.05, the crest coefficient is 0.05-0.25, the circular arc radius of the tooth root is about 0.4-0.8 times of the modulus, a chamfer angle not more than R0.1 is further arranged on the tooth top along the tooth direction, more specifically, the volume occupied by the part of liquid which can not be discharged from the tooth valley also influences the volume efficiency of the product, if gas is mixed in the liquid, the part of liquid is compressed after being brought from the inlet cavity to the outlet cavity, therefore, the part of liquid is used for supplementing the compression of the liquid in the invalid volume, the oil supply amount of the pump is reduced, when the part of liquid returns from the outlet cavity to the inlet cavity, the volume is expanded due to the reduction of pressure, the suction amount of the inlet cavity of the pump is also reduced, the volume is designed to be reduced as much as possible, namely, the oil trapping volume at the tooth valley during meshing, therefore, the tooth direction modification amount is not more than 0.05, the tooth crest coefficient is within the range of 0.05-0.25, the tooth root circular arc radius is about 0.4-0.8 times of modulus, and a chamfer not more than R0.1 is further arranged on the tooth crest along the tooth direction, so that the radial leakage can be further reduced. The bearing has adopted slide bearing, slide bearing has simple structure, overall dimension is little, shock resistance is strong, characteristics such as noise are little, fixed bearing 4 and 3 working end faces of floating bearing are equipped with off-load groove 31 in order to solve the trapped oil problem, have the effect that reduces the volumetric efficiency loss and reduce the noise simultaneously, add extension oil groove 32, with the packing problem under the fluid of satisfying high rotational speed, it has pressure equalizing groove 33 in order to alleviate the radial force to open at the working end face, thereby improve mechanical efficiency, bearing and gear both ends face contact department coating antifriction wear-resistant coating, self-lubricity has been improved.
Furthermore, when the traditional straight gear is in meshing transmission, two teeth are suddenly contacted along the whole tooth width and suddenly leave along the whole tooth width, the noise is high during operation, the flow pulsation is high, trapped oil is generated in the meshing process, serious vibration and impact can be generated, the meshing process of the helical gear 2 is longer than that of the straight gear, the noise is effectively controlled, and the transmission is more stable, so the traditional straight gear is often applied to high-speed and heavy-load products, although the helical gear 2 can reduce the tangential load of each pair of teeth, the helical gear pump still inevitably has radial force and axial force which is not available in the straight gear pump, the axial force of each pair of teeth acting on the helical gear shaft can be composed of two parts, one part is the axial force generated by oil liquid pressure, and the other part is the axial force generated by meshing of the helical gear 2.
In the process of meshing the helical gears 2, the axial force acting on the driven helical gear 2 is composed of two parts, one part is the axial force generated by hydraulic pressure, the other part is the axial force generated by meshing force, the meshing force of the driving shaft helical gear 2A to the driven helical gear 2 is indirectly generated by the hydraulic pressure acting on the driven shaft, the axial force generated by the mutual meshing between the driving shaft helical gear 2A and the driven shaft helical gear 2B is a pair of mutual acting forces, so that the axial force of the driving shaft helical gear 2A acting on the driven shaft helical gear 2B and the hydraulic pressure acting on the driven shaft are a pair of mutual acting forces with equal magnitude and opposite directions, namely the axial force borne on the driven shaft is basically zero, even though the axial force borne on the driven shaft generated by the meshing force is balanced with the hydraulic pressure, the axial force on the driving shaft can be strengthened due to the axial force generated by the hydraulic pressure, therefore, the axial force balance of the helical gear 2 pump mainly refers to the balance of the axial force on the driving shaft.
The helical gear 2 pump comprises a driving helical gear shaft and a driven helical gear shaft, wherein a floating bearing 3 and a fixed bearing 4 are respectively fixed at two ends of the driving helical gear 2, the fixed bearing 4 is fixed in a pump body 1 through a groove arranged in the pump body 1 in a dragging mode, the driving helical gear 2 and the driven helical gear 2 are fixed in the pump body 1 in a suspending mode through the fixed bearing 4, so that the driving helical gear and the driven helical gear can be better and more fully soaked by oil in the pump body 1, and lubricating coatings are further arranged on contact end faces and inner diameter shaft holes of the helical gear 2, the floating bearing 3 and the fixed bearing 4, so that friction energy consumption in the operation process is reduced.
The following measures are mainly adopted for eliminating the axial force:
1. the helical angle is reduced as much as possible during gear design, and ball bearings or thrust bearings are additionally arranged at two ends of the gear to reduce the axial force;
2. the eccentric position of the floating bearing 3 is changed to adjust the pressing force;
3. because the axial force of the fuel pump with the structure is mainly concentrated on the driven floating bearing 3B, the axial force can be counteracted by designing and adjusting the spring pretightening force of the compensation spring 5 below the driven floating bearing 3B when the force of the compensation spring 5 is designed.
When the helical gear 2 is designed, the axial force can be reduced in a manner of reducing a helical angle, the helical gear 2 has more helical angles relative to a straight gear, the helical angle enables the meshing part of the helical gear 2 to generate axial thrust parallel to a driving shaft, the helical gear 2 has larger helical angle, the larger the helical angle is, the larger the axial decomposition force of the helical gear 2 is, the smaller the helical angle is, the axial force can be effectively reduced to a certain extent by reducing the helical angle of the helical gear 2, and in addition, according to the magnitude of the axial force, ball bearings or thrust bearings can be additionally arranged at two ends of the gear shaft, and the axial force can be borne by the ball bearings on the shell; if the axial force is large, the thrust bearing is used to bear the axial force.
As shown in fig. 3 and 4, the floating bearing 3 is installed on one side of the shaft of the helical gear 2, the floating bearing 3 is designed to be eccentric, and the purpose of the floating bearing 3 is to reduce the pressing force which can be adjusted by changing the eccentric position of the floating bearing 3, so that the action line of the pressing force is coincident with the action line of the counter-thrust, and the eccentric position of the floating bearing 3 is determined (X0, Y0). The value range of X0 is (0.1-2) mm, the value range of Y0 is (0.2-3.5), the floating ring of the floating bearing 3 is eccentrically arranged, so that a convergent wedge-shaped gap is formed between a shaft and the floating ring, hydrodynamic lubrication is formed, the shaft diameter is supported by the oil pressure formed by the wedge-shaped oil film, after a shaft neck is stabilized, the oil film pressure is balanced with an external load, when the shaft neck rotates, the floating sleeve rotates due to friction force, oil films with certain bearing capacity are respectively formed inside and outside the floating sleeve in a lubricating state, when the rotating speed of the floating sleeve reaches a certain value, the resultant force and the friction torque acting on the inner surface and the outer surface of the floating sleeve are respectively balanced, when the floating sleeve is eccentrically arranged, the action line of the pressing force is superposed with the action line of a counter-thrust force, the friction torque is increased, the oil films counteract with the axial force generated by the helical gear 2, namely, dynamic pressure lubrication is formed by the eccentric arrangement of the shaft neck of the floating bearing 3, the axial force generated by the helical gear 2 is cancelled.
The floating bearing 3 is usually a bearing which only bears pure radial load, such as a cylindrical roller bearing and a needle roller bearing, because the inner ring of the bearing can move axially relative to the outer ring and does not bear axial load, the floating bearing 3 can have axial floating displacement on the shaft end, a compensation spring 5 is also needed to be arranged on the end surface of the floating bearing 3 to ensure the pre-tightening pressure of the floating bearing 3, the compensation spring 5 is arranged on the end surface of the floating bearing 3, and the end part is limited to move radially through an oil well hole 11 arranged inside the pump body 1, namely when the floating bearing 3 and the gear set are assembled in the pump body 1, the floating spring 5 is arranged between the floating bearing 3 and the pump body 1 to ensure certain pre-tightening pressure, the compensation spring 5 is arranged on the end surface of the floating bearing 3, for example, as shown in fig. 5, 2 groups of 24 compensation springs 5 can be adopted, and each group of 12 are uniformly distributed in each oil well hole 11 within 180 degrees, thus ensuring the required pre-compression force.
More specifically, if there is a pair of 10 standard bevel gears, that is, the angle through which each pair of teeth complete meshing with the driving shaft is 36 ° per tooth, assuming that the inlet pressure of the pump is 1bar and the outlet pressure thereof is 10bar, wherein the hydraulic pressure generated is 9bar, and the hydraulic pressure generated by the known pump is balanced with the axial force generated by meshing with the bevel gears 2, so that the pressure applied to the bevel gears is 9bar and the hydraulic pressure of each tooth is 0.45bar, because the compensation spring 5 is provided to compensate the hydraulic pressure of the pump in the initial process, and is provided for better matching of the bevel gears with each other, but the spring will overturn in the operation process in the meshing area, the compensation spring 5 is provided in the non-meshing area between the bevel gears; the distribution of the floating springs 5 distributed on the end face of the floating bearing 3 on the angle theta should cancel out the hydraulic pressure generated by the pump, that is, the hydraulic pressure needed to be cancelled for the single-sided gear is 4.5bar, so that the hydraulic pressure equivalent to the floating bearing 3 after the springs are installed is assumed to be 0.375bar in the angle range of the angle theta, that is, 12 compensation springs 5 are needed, wherein the angle theta is the angle range of the non-meshed part of the driving shaft helical gear 2A and the driven shaft helical gear 2B, and the value range of the angle theta is (240-320 degrees), and the pre-tightening force generated by the compensation spring 5 arranged on one end side of the floating bearing 3 should satisfy the distribution of the pressure range, that is, the spring force and the distribution thereof needed by the compensation spring 5 can be obtained through the inlet and outlet pressure of the gear pump, the gear tooth number, the rotational meshing angle and the like (as shown in fig. 6). In other words, the position of the compensation spring 5 is in turn related to the position of the oil well bore 11.
Further, the compensation springs 5 may be arranged in a certain manner, such as in a semi-circular equidistant arrangement in fig. 5, a semi-circular non-equidistant arrangement in fig. 6, or a semi-circular non-equidistant staggered arrangement in fig. 7, the oil wells 11 and the compensation springs 5 are arranged in the same manner, and the intervals are not fixed, and the number is not fixed, and the arrangement form is related to the helical angle of the helical gear 2 and the eccentric position of the floating bearing 3, and a staggered arrangement (such as in fig. 7) may be provided, and a stepped compensation spring 5 may be designed, and the generation of the spring force is determined by the specification of the spring and the compression amount of the spring, so that compensation springs 5 of different specifications may be used in different positions, or by changing the depth of the oil wells 11, for example, for springs of the same specification, because one end of the spring is supported by the end face of the floating bearing 3 and the other end is limited in the oil well 11, therefore, the spring force generated by the spring limited in the deeper oil well hole 11 is smaller, the spring force generated by the spring limited in the shorter oil well hole 11 is larger, wherein the distribution position of the oil well hole 11 is consistent with the required action position of the spring force, so that the hydraulic force generated in the initial process can be balanced and offset by the above method, and the working efficiency of the oil pump is improved.
The foregoing has described the principles of use, features and advantages of the invention. The above embodiments and the description of the invention are provided to illustrate the basic principles and features of the invention and, within the scope of the invention concept, to be understood by those skilled in the art from the foregoing description, various modifications may be made to the invention and these modifications are within the scope of the invention as claimed.
Claims (9)
1. The utility model provides an oblique gear pump, its characterized in that, oblique gear pump is equipped with a pair of helical gear (2) of meshing including pump body (1) in the pump body (1), floating bearing (3) and fixed bearing (4) are still respectively installed to the both sides of helical gear, the other end of floating bearing (3) still is equipped with a plurality of compensation spring (5), still be equipped with oil well hole (11) in the pump body (1).
2. The helical gear pump according to claim 1, wherein the aspect ratio of the helical gear is in a range of 0.2 to 1.5, the critical angle of the helix is 10 ° to 30 °, the modification amount in the tooth direction is not more than 0.05, the crest factor is in a range of 0.05 to 0.25, the radius of the circular arc of the tooth root is about 0.4 to 0.8 times, and the tooth tip is further provided with a chamfer not more than R0.1 in the tooth direction.
3. An oblique gear pump and a method of eliminating axial forces thereof according to claim 2, characterized in that the elimination method is a combined arrangement of floating bearings (3), oil wells (11) and compensation springs (5).
4. A gear pump and a method for eliminating axial forces in a gear pump according to claim 3, characterized in that the compensation springs (5) are evenly distributed over the end face of the floating bearing (3).
5. A gear pump and a method for eliminating axial forces in a gear pump according to claim 3, characterized in that the compensation springs (5) are distributed non-uniformly over the end faces of the floating bearing (3).
6. An oblique gear pump and a method for eliminating axial force thereof according to claim 3, wherein said compensation springs (5) are distributed in a staggered manner on the end face of the floating bearing (3).
7. A helical gear pump and a method of eliminating axial forces thereof according to any of claims 4-6, characterized in that the number and arrangement position of the oil wells (11) correspond to the compensating springs (5).
8. An oblique gear pump and a method for eliminating axial force thereof as claimed in claim 7, wherein said floating bearing is eccentrically installed and the eccentric position (X0, Y0) thereof is selected from the range of X0 being (0.1-2) mm and Y0 being (0.2-3.5).
9. An oblique gear pump and an axial force eliminating method thereof according to claim 8, wherein the working end face of the floating bearing (3) is further provided with an unloading groove (31) and a pressure equalizing groove (33), and an extended oil suction groove (32) is additionally arranged, and the end face of the floating bearing (3) is further provided with a high pressure oil passing hole (34).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111327943.1A CN114320888B (en) | 2021-11-10 | 2021-11-10 | Oblique gear pump and method for eliminating axial force thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111327943.1A CN114320888B (en) | 2021-11-10 | 2021-11-10 | Oblique gear pump and method for eliminating axial force thereof |
Publications (2)
| Publication Number | Publication Date |
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| CN114320888A true CN114320888A (en) | 2022-04-12 |
| CN114320888B CN114320888B (en) | 2024-06-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202111327943.1A Active CN114320888B (en) | 2021-11-10 | 2021-11-10 | Oblique gear pump and method for eliminating axial force thereof |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN118049369A (en) * | 2024-03-25 | 2024-05-17 | 福力德泰克(上海)泵业有限公司 | Gear pump with axial compensation function |
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| SU114967A2 (en) * | 1957-02-26 | 1957-11-30 | А.Ф. Осипов | Gear pump for high pressure fluid injection |
| US3937604A (en) * | 1972-04-06 | 1976-02-10 | Joseph Lucas (Industries) Limited | Gear pump or motor with axially movable bearing blocks |
| CN102135094A (en) * | 2011-05-12 | 2011-07-27 | 阜新德尔汽车转向泵有限公司 | Helical gear steering pump |
| DE102013202917A1 (en) * | 2013-02-22 | 2014-08-28 | Robert Bosch Gmbh | Geared machine, particularly gear pump or gear motor, has pressure chamber, in which pressure fluid having low particle concentration is present, and channel, through which pressure chamber is connected with axial force compensating groove |
| JP2016070209A (en) * | 2014-09-30 | 2016-05-09 | ダイキン工業株式会社 | Gear pump or motor |
| CN106481551A (en) * | 2015-08-28 | 2017-03-08 | 河南航天液压气动技术有限公司 | A kind of long-life gear Sliding bearing for pump with spring-compensating |
| CN108799101A (en) * | 2018-06-15 | 2018-11-13 | 哈尔滨理工大学 | A kind of novel floating buss of external gear rotary pump |
| CN109026677A (en) * | 2018-08-28 | 2018-12-18 | 金迈思液压设备（天津）有限公司 | A kind of repairing type helical gear and the helical gear axle sleeve, pressure end cap, gear pump |
| CN211370715U (en) * | 2019-08-30 | 2020-08-28 | 重庆红宇精密工业有限责任公司 | Gear pump with axial clearance compensation device |
-
2021
- 2021-11-10 CN CN202111327943.1A patent/CN114320888B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU114967A2 (en) * | 1957-02-26 | 1957-11-30 | А.Ф. Осипов | Gear pump for high pressure fluid injection |
| US3937604A (en) * | 1972-04-06 | 1976-02-10 | Joseph Lucas (Industries) Limited | Gear pump or motor with axially movable bearing blocks |
| CN102135094A (en) * | 2011-05-12 | 2011-07-27 | 阜新德尔汽车转向泵有限公司 | Helical gear steering pump |
| DE102013202917A1 (en) * | 2013-02-22 | 2014-08-28 | Robert Bosch Gmbh | Geared machine, particularly gear pump or gear motor, has pressure chamber, in which pressure fluid having low particle concentration is present, and channel, through which pressure chamber is connected with axial force compensating groove |
| JP2016070209A (en) * | 2014-09-30 | 2016-05-09 | ダイキン工業株式会社 | Gear pump or motor |
| CN106481551A (en) * | 2015-08-28 | 2017-03-08 | 河南航天液压气动技术有限公司 | A kind of long-life gear Sliding bearing for pump with spring-compensating |
| CN108799101A (en) * | 2018-06-15 | 2018-11-13 | 哈尔滨理工大学 | A kind of novel floating buss of external gear rotary pump |
| CN109026677A (en) * | 2018-08-28 | 2018-12-18 | 金迈思液压设备（天津）有限公司 | A kind of repairing type helical gear and the helical gear axle sleeve, pressure end cap, gear pump |
| CN211370715U (en) * | 2019-08-30 | 2020-08-28 | 重庆红宇精密工业有限责任公司 | Gear pump with axial clearance compensation device |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN118049369A (en) * | 2024-03-25 | 2024-05-17 | 福力德泰克(上海)泵业有限公司 | Gear pump with axial compensation function |
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| Publication number | Publication date |
|---|---|
| CN114320888B (en) | 2024-06-11 |
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