CN201651053U

CN201651053U - Roller bearing without inner ring

Info

Publication number: CN201651053U
Application number: CN2010201715193U
Authority: CN
Inventors: 郭熛; 孙波
Original assignee: PERMCO (TIANJIN) HYDRAULIC Inc Ltd
Current assignee: PERMCO (TIANJIN) HYDRAULIC Inc Ltd
Priority date: 2010-04-27
Filing date: 2010-04-27
Publication date: 2010-11-24
Anticipated expiration: 2020-04-27

Abstract

The utility model relates to a roller bearing without an inner ring, which comprises an outer ring, wherein the inner side of the outer ring is provided with a roller way, and rollers are arranged in the roller way, and are limited to roll in the roller way by a retainer. The edges on both sides of the roller way are radially bended outwards. The rollers slightly swing along with the bending deflection of a gear shaft when the gear shaft is deformed under the stress so as to keep large contact area between the gear shaft and the rollers and prevent uneven stress on the rollers and the edges on both sides of the roller way. The roller bearing without the inner ring solves the technical problem that when the gear shaft is deformed, the stress of the existing bearing is uneven, and pitting and abrasion are easy to generate. The load carrying capability of the bearing is enhanced, and the service life of the bearing is greatly prolonged at the same time, so the service life of the device with the bearing, such as a high-pressure gear pump, is prolonged. The utility model is particularly suitable for high-pressure gear pumps.

Description

A kind of inner ringless roller bearing

Technical field

The utility model relates to a kind of bearing.Specifically a kind of inner ringless roller bearing that is applicable to high-pressure gear pump.

Background technique

High-pressure gear pump adopts gear and gear shaft to carry out transmission, the carrying of high-pressure gear pump and working life not only with the relating to parameters of gear pump, and relevant with the structural parameter and the performance of bearing, we can say that the structural parameter of bearing and performance are to the carrying of high-pressure gear pump with great influence is arranged working life.In high-pressure gear pump, bearing is used for support teeth wheel shaft rotationally, gear shaft is except being subjected to moment of torsion rotates, also be subjected to radial force, under same boundary dimension, the bearing capacity of roller bearing is about 1.5-3 times of ball bearing, big or when impulsive load is arranged in load, should adopt roller bearing, for example in gear pump, the restriction high-pressure gear pump of acceptor center distance generally adopts inner ringless roller bearing.Under the load condition with higher of being born, radial force can make gear shaft produce bending deflection, area of contact between gear shaft and the roller is reduced, the contact stress that bear the edge section of roller increases, the bearing of this structure is easy to generate spot corrosion, wearing and tearing and distortion, thereby influences the working life of gear pump.

Certain piece of patent documentation discloses the roller bearing of a kind of gear pump with no inner ring, this scheme mainly includes bearing outer ring, roller and retainer, outer cylinder mating face at described bearing outer ring is a slight cydariform curved surface, crow flight distance L between the highs and lows of this cydariform curved surface is between the 0.001-0.1 millimeter.Because at the bearing outer ring mating face is a slight cydariform curved surface, this cydariform curved surface is when bearing assembles, because the interference fit between bearing and the bearing support, force the cydariform curved surface of bearing outer ring mating face to become the cydariform curved surface of bearing outer ring and roller surface of contact, when back shaft is subjected to radial force, roller can change along the cydariform curved surface, has increased the surface of contact of back shaft and roller, has prolonged the working life of bearing.Just can reach the cydariform curved surface that makes bearing outer ring and roller surface of contact but this bearing needs to produce bigger distortion when mounted, this technological scheme has improved the requirement that bearing is installed.In addition, because this bearing adopts interference fit to force bearing outer ring and roller surface of contact to become the cydariform curved surface, the degree of crook of this cydariform curved surface can not be controlled accurately.

The model utility content

For this reason, technical problem to be solved in the utility model is to overcome existing inner ringless roller bearing and is subjected to the influence of radial force and the difficult problem of premature failure, and the novel inner ringless roller bearing of a kind of easy manufacturing and installation is provided.

For solving the problems of the technologies described above, inner ringless roller bearing described in the utility model comprises

Outer ring, the inner side surface of described outer ring are raceway;

Some rollers are distributed on the described raceway;

Retainer remains on described roller on the described raceway and to roll;

Described raceway both sides of the edge are to the radially outer direction bending in described outer ring.

The bus of described raceway is level and smooth curve.

Between the two ends of the mid point of described raceway bus and described raceway bus diametrically distance h more than or equal to 0.002mm smaller or equal to 0.012mm.

Technique scheme of the present utility model has the following advantages compared to existing technology: the both sides of the edge of (1) raceway are to radially outer direction bending, when the gear shaft stress deformation, slight swing can take place along with the distortion of gear shaft in roller, make and still keep bigger area of contact between gear shaft and the roller, reduced the contact stress between them, can alleviate the spot corrosion wearing and tearing of bearing, simultaneously because the mating face of its outer ring is the cylndrical surface, there is not projection, need not bigger value of interference fit during installation, therefore overcome the Bearing Installation difficult technologies problem in the background technique.(2) degree of crook of raceway can be controlled accurately by processing technique.(3) radial distance between the two-end-point of the mid point of described raceway bus and bus is 0.002-0.012mm, meets gear shaft bending deflection rule, guarantees bigger area of contact between gear shaft and the roller.

Description of drawings

For the easier quilt of content of the present utility model is clearly understood, according to specific embodiment of the utility model also in conjunction with the accompanying drawings, the utility model is described in further detail, wherein below

Fig. 1 is the sectional view of inner ringless roller bearing described in the utility model;

Fig. 2 is the sectional view of the outer ring of inner ringless roller bearing described in the utility model.

Reference character is expressed as among the figure: 1-outer ring, 2-needle roller, 3-retainer, 4-raceway, the mid point of 5-raceway bus, the end points of 6-raceway bus.

Embodiment

Inner ringless roller bearing comprises the outer ring, and the inner side surface of described outer ring is a raceway, and roller is distributed on the raceway, and is held frame and remains on the described raceway and roll.Gear shaft supports by bearing, and described gear shaft also is subjected to radial force inevitably except the moment of torsion that is subjected to making its rotation.Under the load condition with higher of being born, radial force can make gear shaft produce bending deflection, and the contact stress that bear the edge section of roller and raceway increases, and very easily produces spot corrosion and wearing and tearing.

Fig. 1 is the sectional view of bearing described in the utility model, and Fig. 2 is the sectional view of bearing outer ring 1 described in the utility model.As depicted in figs. 1 and 2, the both sides of the edge of the raceway 4 of described bearing are to radially outer direction bending, and performance is in the drawings, and the bus of raceway 4 be the smooth curve of bending in the bearing outer ring body radially, is cydariform.When gear shaft occurs bending and deformation, roller, be specially needle roller 2 in the present embodiment, along with corresponding slight swing takes place on described raceway 4 for the distortion of gear shaft, thereby guarantee between gear shaft and the described needle roller 2 and bigger area of contact between needle roller 2 and the raceway 4, reduced mutual contact stress, prevented that the edge section of bearing from producing spot corrosion and wearing and tearing because of contact stress is excessive, thereby also prolonged the working life of bearing greatly.Because the bus of the mating face of this bearing outer ring is a straight line,, therefore install also than being easier in that Bearing Installation be need not bigger magnitude of interference on bearing support the time.

In the present embodiment, radial distance between the intermediate portion of described raceway 4 and the both sides of the edge of raceway, show that the radial distance h between the end points 6 of the mid point 5 that is described raceway bus among Fig. 2 and raceway bus is 0.002mm-0.012mm, this is apart from the bending deflection rule that has adapted to gear shaft, when gear shaft occurs bending and deformation, corresponding slight swing can take place in needle roller 2 thereupon, has increased the area of contact between them, has reduced contact stress.The degree of the bending of described raceway 4 is controlled accurately by processing, has overcome in the background technique to force raceway to the uncontrollable defective of the degree of radially inner direction projection by interference fit.

In the above-described embodiments, the radial distance between the end points 6 of the mid point 5 of described raceway bus and raceway bus can also for 0.01mm or 0.012mm or 0.002mm to any numerical value between the 0.012mm.

Obviously, the foregoing description only is for example clearly is described, and is not the qualification to mode of execution.For those of ordinary skill in the field, can also make other changes in different forms on the basis of the above description.Here need not also can't give exhaustive to all mode of executions.And conspicuous variation of being extended out thus or change still are among the protection domain of the invention.

Claims

1. an inner ringless roller bearing comprises

Outer ring, the inner side surface of described outer ring are raceway;

Some rollers are distributed on the described raceway;

Retainer remains on described roller on the described raceway and to roll;

It is characterized in that: described raceway both sides of the edge are to the radially outer direction bending in described outer ring.

2. inner ringless roller bearing according to claim 1 is characterized in that: the bus of described raceway is level and smooth curve.

3. inner ringless roller bearing according to claim 2 is characterized in that: between the two ends of the mid point of described raceway bus and described raceway bus diametrically distance h more than or equal to 0.002mm smaller or equal to 0.012mm.