RU2233388C2 - Hydraulic gear machine - Google Patents

Abstract

FIELD: hydraulic machine building.

SUBSTANCE: proposed hydraulic gear machine contains gears installed in cylindrical bores of housing and at least pair of compensators of end face clearances adjoining end faces of gears and mated through arc-shaped cavity. Machine is provided with seal from rear side of compensators. Arc-shaped cavity is made over entire height of one of compensators. Other compensator mated with first one adjoins end face of gear projecting over end face of other gear. Said compensators, displacing in axial direction relative to each other, adjoin tightly end faces of gears even when gear rims are of different width and when end face of one gear projects over end face of other gear. Bushing without arc-shaped cavity adjoins end face of gear projecting over end face of other gear initially mating without clearances with other bushing and with gears.

EFFECT: increased delivery coefficient of hydraulic machine.

2 cl, 5 dwg

Description

The invention relates to the field of hydraulic machines, in particular to hydraulic machines that can be used in the hydraulic systems of tractors, both general and industrial, excavators, agricultural, road-building and other machines.

Already known gear hydraulic machine, which can be used for the above purposes, containing included in the external gearing of the drive and driven gears installed in the bores of the body of the hydraulic machine, formed by two intersecting cylindrical holes [1]. On one side of the ends of the gears adjoins them a pair of end-face compensators made in the form of bushings. The bushings are interconnected in flat sections on their outer surfaces, and a seal is placed on their rear sides.

During the operation of the sleeve hydraulic machine, the pressure of the working fluid supplied from the output channel of the hydraulic machine into the cavity limited by the seal is pressed to the ends of the gears, thereby sealing the working chamber of the hydraulic machine.

However, due to the fact that within the tolerances the gear crowns can be made different in width, the end face of one gear will protrude above the end of the other gear and, therefore, the end face of one of the bushes will not fully seal the end of the corresponding gear, which will lead to a decrease in the hydraulic machine feed.

In another known hydraulic machine containing external gears installed in the cylindrical bores of the housing, at least a pair of end-face compensators are interconnected by arcuate recesses on their outer surfaces [2]. On the back of these compensators, adjacent to the ends of the gears, a seal is placed.

Thus, due to the coupling of the compensators with each other in an arcuate recess, each of them, having the ability to move in the axial direction, will be close to the end of the corresponding gear with its end face, increasing the flow of the hydraulic machine. However, on the other hand, the feed of the hydraulic machine will be significantly reduced due to the coupling of the compensators together in one arcuate recess and the formation of a gap in the other recess, which reports directly the low and high pressure zones, since it is impossible to make two identical ones in two different compensators and the location of the arched recesses.

The basis of the invention is the task of creating a gear hydraulic machine, in which, due to changes in the coupling of the compensators with each other and with the gears, the gaps in these interfaces would be minimized and the feed coefficient of the hydraulic machine would increase.

This problem is solved in that in a gear hydraulic machine containing external gears installed in the cylindrical bores of the housing, at least a pair of end-face compensators, interconnected by an arcuate recess adjacent to the ends of the gears, and a seal on the back of the compensators, according to the invention an arcuate recess is made along the entire height of one of the compensators, and the other compensator conjugated with it is adjacent to the end of the gear protruding above the end of the other gear.

Thus, by pairing the compensators with each other along only one arcuate recess and along the entire height of the compensator and placing the compensator without a recess from the side of the gear end, projecting above the end of the other gear, it is achieved that the compensators are initially mated with each other and gears without gaps, increasing in operation, the feed coefficient of the hydraulic machine.

In addition, it is advisable that in the design of the hydraulic machine with two pairs of compensators adjacent to both ends of the gears and the bores of the housing, made in the form of wells, compensate for the possibility of their different depths, compensate the end gaps without arched recesses to be conjugated with opposite ends of different gears .

In the following, the invention is illustrated by an example of its specific implementation and drawings, where:

figure 1 shows a longitudinal section of one embodiment of a hydraulic machine along the axes of the gears;

figure 2 shows a cross section of a hydraulic machine along aa from figure 1;

figure 3 shows an enlarged view of a local view of B from figure 1;

figure 4 shows a longitudinal section along the axes of the gears of another embodiment of the hydraulic machine, where the exaggerated view shows the location of the compensators and gears with different depths of bores under them in the housing;

figure 5 shows a cross section of a hydraulic machine on BB in figure 4.

The gear hydraulic machine contains the leading 1 and driven 2 gears, made in conjunction with the pins 3 and 4. The driving gear 1 also has a drive shaft 5, sealed with a sleeve 6. Gears 1 and 2 together with end-face compensators made in the form of bushings 7 and 8, in of which the pins 3 and 4 of gears 1 and 2 are located, are installed in the inner chamber of the casing 9 of the hydraulic machine, formed by two cylindrical bores 10 and 11, see figure 1. At their other ends, the pins 3 and 4 of the gear are mounted in sliding bearings 12 and 13, which are pressed into the housing 9 of the hydraulic machine, and the ends of the gears 1 and 2, on this side, are adjacent to the antifriction plate 14.

The bushings 7 and 8, within the gaps, are movable in the radial, axial directions and are interconnected by an arcuate recess 15, made in the sleeve 8 along its entire height. The other sleeve 7 is installed so that it adjoins the end of the gear, which protrudes above the end of the other gear, in this embodiment, to the end of gear 1, the crown of which is wider than the crown of gear 2, see FIG. 3.

On the back of the bushings 7 and 8 in the cover 16 there is a seal 17, which seals the compensation chamber 18.

Gear hydraulic machine in pump mode operates as follows.

When the gears 1 and 2 are brought into rotation by the drive shaft 5, a vacuum is formed in the troughs of the outgoing teeth of the gears, as a result of which the working fluid enters the inlet channel 19, fills the interdental spaces of the gears, is transferred to the high pressure zone and is replaced by the teeth entering the gearing into the outlet channel 20, see FIG. 2, where the input and output channels are shown by a dashed line.

The working fluid under pressure from the outlet channel 20 enters from the high-pressure zone into the compensation chamber 18, which is limited by a seal 17 located in the cover 16.

Under the influence of the pressure of the working fluid in the compensation chamber 18, the bushings 7 and 8 advance axially and are pressed against the lateral surfaces of gears 1 and 2 with their ends, and those, in turn, against the antifriction plate 14, sealing them and the pump working chamber.

Since the bushings 7 and 8 are interconnected by an arcuate recess 15, made along the entire height of the sleeve 8, then, shifting in the axial direction relative to one another, they fit snugly against the ends of the gears even when the gear crowns have different widths and when the end face one gear protrudes above the end of the other gear. At the same time, the sleeve without an arcuate recess adjoins the end of the gear protruding above the end of the other gear, initially mating with the other sleeve and gears, without gaps, increasing the feed coefficient of the hydraulic machine in operation.

In another embodiment of the hydraulic machine shown in FIGS. 4 and 5, such an embodiment of the bushings, when their additional pair 21 and 22 is located at other ends of the gears, can compensate for the execution of cylindrical bores 10 and 11 in the housing 9 with different depths. In this case, the bushings without arcuate recesses are made paired with the opposite ends of the various gears, see figure 4, where in an exaggerated form shows the location of the bushings and gears.

When operating in the hydraulic motor mode, the working fluid supplied under high pressure to the output channel 20 acts on the gear teeth, rotating them and overcomes the load applied to the drive shaft 5.

Otherwise, the operation of the hydraulic machine in the hydraulic motor mode is similar to its operation in the pump mode.

Sources of information

1. SU 723218 A, 04/05/1980, F 04 C 2/04.

2. SU 794252 A, 01/07/1981, F 04 C 2/04.

Claims (2)

1. A gear hydraulic machine containing external gears installed in the cylindrical bores of the housing, at least a pair of end-face compensators, interconnected by an arc-shaped recess, adjacent to the ends of the gears and a seal on the back of the compensators, characterized in that the arc-shaped recess is made according to the entire height of one of the compensators, and the other compensator coupled with it is adjacent to the end of the gear protruding above the end of the other gear. 2. The gear hydraulic machine according to claim 1, characterized in that the compensators for end clearances without arched recesses are associated with opposite ends of various gears.

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