CN101368552B - Heeling moment full-balancing shaft distribution mechanism and bidirectional variable radial ball piston pump - Google Patents

Abstract

The invention is an axial flow distribution mechanism and a two-way variable radial ball pump with fully balanced tilting moments. Through the oil channel and thin-walled damping hole in the distribution shaft, the high-pressure oil discharge hole and the low-pressure side balance oil tank and the low-pressure oil suction hole are communicated with the high-pressure side balance oil tank, and the damping effect of the thin-walled damping hole is used to adjust the flow distribution pair to a balanced state , to maintain a constant distribution gap. An oil groove corresponding to the high and low pressure oil holes of the distribution shaft is opened on the right end surface of the end cover to balance the axial hydraulic pressure on the distribution shaft, so the distribution shaft is not affected by the tilting moment. The ball plunger is used instead of the plunger, so that the radial size of the two-way variable radial ball plunger pump is small and the structure is compact. It can realize high speed, large displacement, simple variable mechanism and high reliability.

Description

Axial flow distribution mechanism with fully balanced tilting moment and bidirectional variable radial ball pump

Technical field:

The invention belongs to the technical field of hydraulic machinery, and relates to an axial flow distribution mechanism with fully balanced tilting moments and a bidirectional variable radial ball pump using the mechanism, which is suitable for high temperature, high pressure, high speed and large displacement working environments.

Background technique:

In the prior art, due to the processing and assembly errors between the distribution shaft and the cylinder body, the radial piston pump with axial distribution will cause the wear of the distribution pair, so that the distribution gap will continue to increase, and the leakage will become more and more serious, which greatly affects the radial plunger. The volumetric efficiency of the pump; if the design of the distribution gap is too small, the volumetric efficiency of the pump can be improved, but the mechanical efficiency of the pump is greatly reduced, and even the phenomenon of shaft locking of the distribution pair may occur, causing the pump to fail to work normally. Moreover, the flow distribution bearing of the existing shaft distribution radial plunger pump is subject to a large hydraulic pressure and tilting moment, which makes the flow distribution shaft and the surface of the cylinder body eccentrically worn, thereby shortening the service life of the radial plunger pump. Due to the longer plunger, the radial dimension of the radial piston pump is larger, and the sliding shoe pair is more sensitive to the linear velocity, which limits the increase in the speed of the radial piston pump.

Invention content:

The purpose of the present invention is to realize the balance of the radial and circumferential forces of the distribution shaft, so that the distribution shaft is not affected by the tilting moment, and a shaft distribution mechanism with full balance of the tilting moment is designed, and according to this mechanism, a Two-way variable radial ball pump. The distribution shaft is in a floating state, and the hydraulic pressure and torque inside the pump all act on the bearing through the cylinder. The working principle of the tilting moment full balance shaft distribution mechanism designed by the present invention is: the low pressure oil suction hole communicates with the high pressure side balance oil groove through the high pressure side communication oil channel and the thin wall damping hole in the distribution shaft, and the other low pressure side communicates with the oil channel The high-pressure oil discharge hole communicates with the balance oil tank on the low-pressure side with the thin-walled damping hole. Using the damping effect of the thin-walled damping hole, when the flow distribution gap increases, the oil pressure in the high-pressure and low-pressure side balance oil tank decreases, and when the flow distribution gap decreases Hours, the oil pressure of the balance oil tank on the high and low pressure sides increases, both of which will make the distribution pair adjust to a balanced state and maintain a constant distribution gap. The oil groove corresponding to the high and low pressure oil holes of the distribution shaft is opened on the right end surface of the end cover to balance the axial hydraulic pressure on the distribution shaft, so the distribution shaft is not affected by the tilting moment. The leftward axial hydraulic pressure acting on the end cover is transmitted to the housing through the mandrel, lock nut and flow distribution interface. In the design, the length of the mandrel step is guaranteed to be greater than the length of the distribution shaft, so that a certain gap is maintained between the end cover and the distribution shaft, so the distribution shaft is in a floating state. At the same time, two cylindrical pins are installed between the distribution shaft and the distribution interface to prevent the distribution shaft from rotating in the circumferential direction.

Beneficial effect:

The invention can automatically adjust the flow distribution pair to a balanced state through the balance oil groove on the flow distribution shaft and the thin-walled damping hole in the communication oil channel, and maintain a constant flow distribution gap. At the same time, the plunger in the radial plunger pump is replaced by a ball plunger, so that the radial size of the two-way variable radial ball plunger pump is reduced and the structure is compact. Since the sliding shoe pair sensitive to linear velocity in the plunger pump is replaced by the rolling friction pair of the ball plug and the action ring, a high working speed can be achieved. The displacement of the pump can be increased by arranging multiple rows of ball plugs while keeping the radial dimension unchanged, so it is easy to achieve a large displacement. The displacement can be easily changed by changing the eccentric distance between the action ring and the cylinder body, and the variable mechanism is simple and reliable. Due to the cancellation of the pair of sliding shoes, the number of key parts and the number of friction pairs are reduced, so it has higher reliability.

Description of drawings:

Fig. 1 is a schematic diagram of the internal structure of the two-way variable radial ball pump of the present invention.

FIG. 2 is a schematic diagram of the A-A section structure in FIG. 1 .

Fig. 3 is a schematic diagram of the B-B sectional structure in Fig. 1 .

In the figure: 1-front cover, 2-left bearing cover, 3-deep groove ball bearing, 4-end cover, 5-mandrel, 6-lock nut, 7-input shaft, 8-cylinder block, 9-pin , 10-straight pin, 11-pump housing, 12-right bearing cap, 13-cylindrical roller bearing, 14-balance oil tank on high pressure side, 14'-balance oil tank on low pressure side, 15-distribution shaft, 16-distribution interface, 17-straight pin, 18-flow sleeve, 19-oscillating shaft, 20-left bushing, 21-right bushing, 22-handwheel, 23-screw, 24-round nut, 25-outer ring, 26-inner Action ring, 27-ball plug, 28-high pressure oil discharge hole, 28'-low pressure oil suction hole, 29-thin-walled damping hole on high-pressure side, 29'-thin-walled damping hole on low-pressure side, 30-communicating oil passage on high-pressure side, 30 '-The low-pressure side communicates with the oil passage.

The bidirectional variable radial ball pump designed according to the tilting moment full balance shaft flow distribution mechanism of the present invention comprises a front cover (1); a pump casing (11); used for positioning the front cover (1) and the pump casing (11) cylindrical pin (10); used to support the deep groove ball bearing (3) placed in the front cover (1) of the cylinder body (8) and the cylindrical roller bearing (13) in the pump housing (11); as a pump The handwheel (22), screw rod (23) and round nut (24) of the variable mechanism; the outer action ring (25) snapped into the round nut (24) and the inner action ring (26) placed therein; The swing shaft (19) in the action ring (25); the left shaft sleeve (20) and the right shaft sleeve (21) placed on the swing shaft (19) for the axial positioning of the outer action ring (25); The pin (9) for the axial positioning of the swing shaft (19) in the pump casing (11); the distribution shaft (15) located at the axis of the cylinder body (8); the distribution port located on the right end of the distribution shaft (15) ( 16); the left bearing cover (2) located at the left end of the deep groove ball bearing (3); the right bearing cover (12) located at the right end of the cylindrical roller bearing (13); the ball plug (27) placed in the cylinder body (8) ); the input shaft (7) used to drive the cylinder (8); the cylindrical pin (17) placed in the distribution shaft (15) and the distribution interface (16); the distribution sleeve ( 18); the mandrel (5), the end cover (4) and the lock nut (6) that are positioned at the axial center of the flow distribution shaft (15). Among the above components, the input shaft (7) and the cylinder body (8) are coaxial, the top of the outer action ring (25) is in contact with the round nut (24), and there are two high-pressure The oil discharge hole (28) and two low pressure oil suction holes (28'), the high and low pressure sides of the distribution shaft (15) are respectively provided with two semi-annular high pressure side balance oil grooves (14) and low pressure side balance oil grooves (14 '), at the same time, there are two high-pressure side communication oil passages (30) for communicating the low-pressure oil suction hole (28') and the high-pressure side balance oil tank (14), and two high-pressure side communication oil passages (30) for communicating the high-pressure oil discharge hole (28) and the low-pressure side The low-pressure side communication oil passage (30') of the balance oil tank (14') is respectively equipped with thin-walled damping holes (29) and (29 '). It is characterized in that the plunger is replaced by a ball plug (27).

The two-way variable radial piston pump thus constituted, the radial hydraulic force and axial hydraulic force on the distribution shaft (15) are balanced, so it is not affected by the tilting moment, and the distribution shaft (15) is in a floating state. state, prolonging the service life of the two-way variable radial ball pump. The pump has a simple and compact structure, low difficulty in disassembly and assembly, and is convenient for maintenance and repair.

Detailed ways:

Referring to Fig. 1 and Fig. 2, the input shaft (7) drives the cylinder body (8) to rotate, and the ball plug reciprocates along the axis of the cylinder body hole while rotating with the cylinder body, so that the ball plug (27), the cylinder body hole and the The volume of the working chamber between the flow distribution mechanisms changes to complete the process of oil absorption and oil discharge. The ball plug (27) is in contact with the inner surface of the inner acting ring (26), and the outer acting ring (25) is controlled by the hand wheel (22), so that the inner and outer acting rings can swing around the swing shaft (19) to achieve bidirectional variable. Variable mechanism mainly is made up of swing shaft (19), hand wheel (22), screw rod (23) and round nut (24). The flow distribution interface (16) is fixed on the pump casing (11), and the flow distribution shaft (15) does not rotate with the cylinder body (8) through two cylindrical pins (17).

Referring to Fig. 2 and Fig. 3, there are four through holes in the section of the distribution shaft (15), among which (28) are two high-pressure oil discharge holes, (28') are two low-pressure oil suction holes, and the high-pressure side communicates with the oil passage (30 ) communicates with the low-pressure oil suction hole (28') and the high-pressure side balance oil groove (14), and the low-pressure side communicates with the oil passage (30') to communicate with the high-pressure oil discharge hole (28) and the low-pressure side balance oil groove (14'). ), (30') are respectively provided with thin-walled damping holes (29) and (29'). Utilizing the damping effect of the thin-walled damping hole, when the flow distribution gap increases, the oil pressure of the balance oil tank on the high and low pressure sides decreases, and when the flow distribution gap decreases, the oil pressure of the balance oil tank on the high and low pressure side increases. Adjust the distribution pair to a balanced state and maintain a constant distribution gap. An oil groove corresponding to the high and low pressure oil holes of the distribution shaft is opened on the right end surface of the end cover (4) to balance the axial hydraulic pressure on the distribution shaft (15), so the distribution shaft (15) is not affected by the tilting moment. In the design, the length of the step of the mandrel (5) is guaranteed to be greater than the length of the distribution shaft (15), so that a certain gap is maintained between the end cover (4) and the distribution shaft (15), so that the distribution shaft (15) is in a floating state. The eccentric wear of the flow distribution shaft (15) and the flow distribution sleeve (18) is avoided, and the service life of the pump is improved.

Claims (1)

1. A two-way variable radial ball pump with an axial flow distribution mechanism that is fully balanced with tilting moments, mainly including a front cover (1), a pump housing (11), a cylinder body (8), and an end cover (4). It is characterized in that: the front cover (1) and the pump casing (11) are positioned by cylindrical pins (10), and the cylinder body (8) is mounted on the front cover (1) by deep groove ball bearings (3) and cylindrical roller bearings (13). ) and the pump casing (11), the distribution shaft (15) is installed at the axis of the cylinder body (8), the mandrel (5) is installed at the axis of the distribution shaft (15), and the right end of the distribution shaft (15) is installed There is a flow distribution interface (16), and a ball plug (27) is installed in the cylinder body (8); the input shaft (7) is connected with the cylinder body (8); The pump casing (11) is equipped with: the handwheel (22), the screw (23) and the round nut (24) of the pump variable mechanism, the outer action ring (25) snapped into the round nut (24) and placed outside The inner action ring (26) in the action ring, the swing shaft (19) placed in the outer action ring (25), the left shaft placed on the swing shaft (19) for the axial positioning of the outer action ring (25) sleeve (20) and right sleeve (21), pin (9) for axial positioning of the swing shaft (19) in the pump housing (11), left bearing cover ( 2), the right bearing cap (12) located at the right end of the cylindrical roller bearing (13); a cylindrical pin (17) is installed between the distribution shaft (15) and the distribution interface (16); a distribution sleeve is installed in the cylinder body (8) (18); said end cover (4) and lock nut (6) are installed at the axis of distribution shaft (15); The section of the distribution shaft (15) has four through holes, including two high-pressure oil discharge holes (28) and two low-pressure oil suction holes (28'), and the high-pressure side communicates with the oil channel (30) to communicate with the low-pressure oil suction hole (28' ) and the high-pressure side balance oil groove (14) of the distribution shaft, the low-pressure side communication oil passage (30') communicates with the high-pressure oil discharge hole (28) and the low-pressure side balance oil groove (14') of the distribution shaft, and the high-pressure side communication oil passage ( 30) and the low-pressure side communication oil passage (30') are respectively provided with thin-walled damping holes (29, 29'); An oil groove corresponding to the high and low pressure oil holes of the distribution shaft is opened on the right end surface of the end cover (4) to balance the axial hydraulic pressure on the distribution shaft (15), so the distribution shaft (15) is not affected by the tilting moment.

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