CN216812969U - Improved reversing mechanism for displacement control - Google Patents
Improved reversing mechanism for displacement control Download PDFInfo
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- CN216812969U CN216812969U CN202122928646.4U CN202122928646U CN216812969U CN 216812969 U CN216812969 U CN 216812969U CN 202122928646 U CN202122928646 U CN 202122928646U CN 216812969 U CN216812969 U CN 216812969U
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Abstract
The utility model relates to a hydraulic pump, in particular to an improved reversing mechanism for controlling displacement, which comprises a valve body and a valve core, wherein a left axial blind hole and a right axial blind hole are respectively formed along the axial direction of the valve core, a left radial hole and a left radial throttling hole which are communicated with the left axial blind hole and a right radial throttling hole which are communicated with the right axial blind hole are respectively formed along the radial direction of the valve core, the left radial hole and the right radial hole are respectively positioned at the outer sides of a left double convex ring and a right double convex ring, and the left radial throttling hole and the right radial throttling hole are respectively positioned between grooves of the left double convex ring and the right double convex ring. According to the utility model, the machining precision and the production cost can be greatly reduced by changing 0 cover into the positive cover, and meanwhile, the slope of a servo pressure curve along with the change of current is more gentle when the servo valve is changed from a middle position to a working position by adding the left axial blind hole, the right axial blind hole, the left radial hole, the right radial hole, the left radial orifice and the right radial orifice, the impact of the rising of the servo pressure is reduced, and the stability of a servo system is improved.
Description
Technical Field
The utility model relates to a hydraulic pump, in particular to an improved reversing mechanism for displacement control.
Background
In a closed hydraulic pump, a reversing mechanism is required to realize bidirectional control of the displacement from zero to the maximum or from the maximum to the zero, and hydraulic oil is required to push a servo mechanism so as to push a swash plate to swing, so that the displacement is changed.
A traditional reversing mechanism for displacement control is shown in fig. 1-3, and comprises a valve body 1, wherein an inner cavity of the valve body 1 is matched with a valve core 2, two ends of the inner cavity of the valve body 1 are respectively communicated with an opening a of a left proportional solenoid valve and an opening B of a right proportional solenoid valve, a left annular groove 11 and a right annular groove 12 are formed in the cavity wall of the inner cavity of the valve body 1, a left hydraulic oil inlet 13 and a right hydraulic oil inlet 14 are respectively opened in the left annular groove 11 and the right annular groove 12, a left servo mechanism oil duct 15 and a right servo mechanism oil duct 16 are respectively opened in the inner cavities of the valve body at the inner sides of the left annular groove 11 and the right annular groove 12, the left annular groove 11 and the right annular groove 12 are in mirror symmetry about a center line M thereof, the left servo mechanism oil duct 15 and the right servo mechanism oil duct 16 are in mirror symmetry about the center line M thereof, and the widths of the left annular groove 11 and the right annular groove 12 are larger than the diameters of the left servo mechanism oil duct 15 and the servo mechanism oil duct 16; the valve core 2 is provided with a left double convex ring 21 and a right double convex ring 22, the left double convex ring 21 and the right double convex ring 22 are in mirror symmetry about a central line N, circumferential circular surfaces of the left double convex ring 21 and the right double convex ring 22 are in sealing fit with an inner cavity of the valve body 1, and the widths of the left double convex ring 21 and the right double convex ring 22 are equal to or slightly larger than the diameters of the servo mechanism left oil passage 15 and the servo mechanism right oil passage 16. Theoretically: when the valve core 2 is positioned in the middle position, namely the center line M and the center line N are coincident, the outer rings of the left double convex ring 21 and the right double convex ring 22 simultaneously cut off the communication between the hydraulic oil left inlet 13 and the servo mechanism left oil passage 15, and the communication between the hydraulic oil right inlet 14 and the servo mechanism right oil passage 16, namely the valve core and the valve body are set to be 0 cover. However, due to insufficient machining precision, it cannot be guaranteed that the outer rings of the left double-convex ring 21 and the right double-convex ring 22 are simultaneously closed or communicated with the oil ducts 15 and 16, so that the outer ring of the convex ring 21 is communicated with the oil duct opening 15, the outer ring of the convex ring 22 is closed with the oil duct opening 16 or the outer ring of the convex ring 21 is closed with the oil duct opening 15, and the outer ring of the convex ring 22 is communicated with the oil duct opening 16. Hydraulic oil at the conduction end enters two ends of the servo piston, and the other end of the servo piston is sealed, so that pressure difference exists between the two servo ends, the servo piston is caused to slightly move, the swash plate is slightly swung, and the action of the hydraulic pump is inaccurate. The outer ring of the left double-convex ring 21 or the right double-convex ring 22 cannot completely cut off the communication between the hydraulic oil left inlet 13 and the servo mechanism left oil duct 15 or between the hydraulic oil right inlet 14 and the servo mechanism right oil duct 16, and a small amount of hydraulic oil enters the servo mechanism left oil duct 15 or the servo mechanism right oil duct 16, so that the servo mechanism slightly moves, the swash plate slightly swings, and the action of the hydraulic pump is misaligned. The solution is certainly to improve the precision of machining and assembly, but this will bring about a reduction in efficiency and an increase in cost.
SUMMERY OF THE UTILITY MODEL
In order to overcome the defects of the prior art, reduce the processing difficulty and improve the production efficiency, the utility model discloses an improved reversing mechanism for displacement control, which adopts the technical scheme that:
the utility model provides a modified is used for discharge capacity control's reversing mechanism, including valve body and case, different with prior art, set up left axial blind hole and right axial blind hole respectively along the case axial, set up respectively along the case radially with the communicating left radial hole of left axial blind hole and left radial orifice, with the communicating right radial hole of right axial blind hole and right radial orifice, left radial hole and right radial hole are located the outside of left biconvex ring and right biconvex ring respectively, left radial orifice and right radial orifice are located the recess of left biconvex ring and right biconvex ring respectively. The 0 mask from the prior art is changed to a positive mask.
Further, the diameters of the left radial throttle hole and the right radial throttle hole are within 0.5 mm.
Compared with the prior art, the servo valve has the advantages that the machining precision and the production cost can be greatly reduced by changing the valve core structure from 0 covering to positive covering, and meanwhile, the slope of a servo pressure curve along with the change of current is smoother when the servo valve is changed from a middle position to a working position, the rising impact of the servo pressure is reduced, and the stability of a servo system is improved by increasing the left axial blind hole, the right axial blind hole, the left radial hole, the right radial hole, the left radial orifice and the right radial orifice.
Drawings
Fig. 1 is a schematic structural view of a valve body of a conventional reversing mechanism for displacement control.
Fig. 2 is a schematic structural diagram of a valve core of a conventional reversing mechanism for displacement control.
Fig. 3 is a schematic structural diagram of a valve core of a conventional reversing mechanism for displacement control in a neutral position of a valve body.
Fig. 4 is a schematic view of the valve cartridge of the present invention.
Fig. 5 is a schematic structural view of the valve core of the present invention in a neutral position in the valve body.
Fig. 6 is a schematic structural view of the valve core of the present invention at the right position of the valve body.
Fig. 7 is a schematic structural diagram of the valve core of the utility model at the left position of the valve body.
Detailed Description
The utility model will be further explained with reference to the drawings.
An improved reversing mechanism for displacement control comprises a valve body 1 and a valve core 2, wherein the valve body 1 is basically the same as the prior art, referring to fig. 1, the left end of an inner cavity of the valve body 1 is communicated with an A port of a left proportional electromagnetic valve, the right end of the inner cavity of the valve body 1 is communicated with a B port of a right proportional electromagnetic valve, a left annular groove 11 and a right annular groove 12 are formed in the cavity wall of the inner cavity of the valve body 1, a left hydraulic oil inlet 13 and a right hydraulic oil inlet 14 are respectively opened in the left annular groove 11 and the right annular groove 12, a left servo mechanism oil duct 15 and a right servo mechanism oil duct 16 are respectively opened in the inner cavities of the valve body at the inner sides of the left annular groove 11 and the right annular groove 12, the left annular groove 11 and the right annular groove 12 are in mirror symmetry about a valve body center line M, the left servo mechanism oil duct 15 and the right servo mechanism oil duct 16 are in mirror symmetry about the valve body center line M, and the widths of the left annular groove 11 and the right annular groove 12 are larger than the diameters of the left servo mechanism oil duct 15 and the servo mechanism right oil duct 16; the valve core 2 comprises a part of structure in the prior art, for example, the valve core 2 is provided with a left double convex ring 21 and a right double convex ring 22, the left double convex ring 21 and the right double convex ring 22 are in mirror symmetry about a central line N of the valve core, circumferential circular surfaces of the left double convex ring 21 and the right double convex ring 22 are in sealing fit with an inner cavity of the valve body 1, and the widths of the left double convex ring 21 and the right double convex ring 22 are equal to or slightly larger than the diameters of the left oil duct 15 and the right oil duct 16 of the servo mechanism; the outer sides of the left radial hole 25 and the right radial hole 26 are respectively provided with a left outer convex ring 29 and a right outer convex ring 30, the left outer convex ring 29 and the right outer convex ring 30 are in mirror symmetry about a central line N of the valve core, the circumferential circular surfaces of the left outer convex ring 29 and the right outer convex ring 30 are in sealing fit with an inner cavity of the valve body 1, the width of a groove between the left outer convex ring 29 and the left double convex ring 21 is larger than the width of the left annular groove 11 of the valve body 1, and the width of a groove between the right outer convex ring 30 and the right double convex ring 22 is larger than the width of the right annular groove 12 of the valve body 1.
The improved point of the present embodiment is that the valve core, as shown in fig. 4, is provided with a left axial blind hole 23 and a right axial blind hole 24 along the axial direction of the valve core 2, a left radial hole 25 and a left radial orifice 27 communicated with the left axial blind hole 23, and a right radial hole 26 and a right radial orifice 28 communicated with the right axial blind hole 24 along the radial direction of the valve core 2, the left radial hole 25 and the right radial hole 26 are respectively positioned at the outer sides of the left double-convex ring 21 and the right double-convex ring 22, and the left radial orifice 27 and the right radial orifice 28 are respectively positioned between the grooves of the left double-convex ring 21 and the right double-convex ring 22. The diameters of the left radial throttle hole 27 and the right radial throttle hole 28 are within 0.5mm, and are 0.5mm in this embodiment. The valve core and the valve body are arranged to be positively covered.
The ports A and B at the two ends of the valve body 1 are respectively connected with a proportional electromagnetic valve, the proportional electromagnetic valve is electrified to convert an electric signal into mechanical force, the valve core 2 is pushed to move, the electromagnetic force is balanced with the spring force of a matching mechanism, and therefore the linear change of the valve core position along with the linear change of the current and the linear change of the corresponding servo force is realized, and the linear control of the displacement is realized.
When the valve core 2 is in the middle position, i.e. the centre line M and the centre line N coincide, as shown in fig. 5, the valve core and the valve body are in the covering state, the hydraulic oil cannot flow directly from 11 to 15, and the other side cannot flow from 12 to 16; but may pass 25/23/27 to 15 and the other end 26.24.28 to 16 to reach both ends of the servo piston. The pressures at the two servo ends are the same, and no difference exists. Therefore, even if the machining precision is insufficient, if the outer ring of the left double-convex ring 21 cannot completely have a small amount of hydraulic oil to enter the left oil passage 15 of the servo mechanism, the small amount of hydraulic oil entering the left oil passage 15 of the servo mechanism returns to the left hydraulic oil inlet 13 from the left radial throttle hole 27, the left axial blind hole 23 and the left radial hole 25 under the condition that the servo mechanism is not pushed to do work, so that the servo mechanism is not subjected to abnormal motion, and the stability of the hydraulic pump action caused by the middle position is ensured.
As shown in fig. 6, when the left proportional solenoid valve extends out to the right, the valve core 2 is in the right position, the outer ring of the left double-convex ring 21 completely cuts off the communication between the hydraulic oil left inlet 13 and the servo mechanism left oil passage 15, although a small amount of hydraulic oil still enters the servo mechanism left oil passage 15 from the left radial throttle hole 27; the outer ring of the right double-convex ring 22 is located in the range of the servo mechanism right oil duct 16, a large amount of hydraulic oil enters the servo mechanism right oil duct 16 from the hydraulic oil right inlet 14, and a small amount of hydraulic oil enters the servo mechanism right oil duct 16 from the right radial throttle hole 28, but the force of the hydraulic oil entering the servo mechanism left oil duct 15 from the left radial throttle hole 27 and the force of the hydraulic oil entering the servo mechanism right oil duct 16 from the right radial throttle hole 28 are mutually offset, so that the hydraulic oil entering the servo mechanism right oil duct 16 from the hydraulic oil right inlet 14 cannot be affected. The servo mechanism acts accurately, and the stability of the action of the hydraulic pump is ensured.
As shown in fig. 7, when the right proportional solenoid valve extends out to the right, the valve core 2 is in the left position, and the outer ring of the right double-convex ring 22 completely cuts off the communication between the hydraulic oil right inlet 14 and the servo mechanism right oil passage 16, although a small amount of hydraulic oil still enters the servo mechanism right oil passage 16 from the right radial throttle hole 28; the outer ring of the left double-convex ring 21 is located in the range of the servo mechanism left oil passage 15, a large amount of hydraulic oil enters the servo mechanism left oil passage 15 from the hydraulic oil left inlet 13, and a small amount of hydraulic oil enters the servo mechanism left oil passage 156 from the left radial throttle hole 27, but the force of the hydraulic oil entering the servo mechanism left oil passage 15 from the left radial throttle hole 27 and the force of the hydraulic oil entering the servo mechanism right oil passage 16 from the right radial throttle hole 28 are mutually offset, so that the hydraulic oil entering the servo mechanism left oil passage 15 from the hydraulic oil left inlet 13 is not affected, the servo mechanism acts accurately, and the stability of the hydraulic pump action is ensured.
The foregoing is only a preferred embodiment of the present invention, and is not intended to limit the present invention in any way; those skilled in the art can make many possible variations or modifications to the utility model using the methods and techniques disclosed above, or to modify equivalent embodiments without departing from the scope of the utility model. Any simple modification, equivalent replacement, equivalent change and modification made to the above embodiments according to the technical essence of the present invention are still within the protection scope of the technical scheme of the present invention.
Claims (4)
1. An improved reversing mechanism for displacement control comprises a valve body (1) and a valve core (2), and is characterized in that: set up left axial blind hole (23) and right axial blind hole (24) respectively along case (2) axial, radially set up respectively with left axial blind hole (23) communicating left radial hole (25) and left radial orifice (27), with right axial blind hole (24) communicating right radial hole (26) and right radial orifice (28) along case (2), left radial hole (25) and right radial hole (26) are located the outside of left biconvex ring (21) and right biconvex ring (22) respectively, left radial orifice (27) and right radial orifice (28) are located the recess of left biconvex ring (21) and right biconvex ring (22) respectively.
2. An improved reversing mechanism for displacement control according to claim 1, wherein: the diameters of the left radial throttle hole (27) and the right radial throttle hole (28) are within 2 mm.
3. An improved reversing mechanism for displacement control according to claim 1, wherein: the left end of an inner cavity of the valve body (1) is communicated with a port A of the left proportional electromagnetic valve, the right end of the inner cavity of the valve body (1) is communicated with a port B of the right proportional electromagnetic valve, a left annular groove (11) and a right annular groove (12) are formed in the wall of the inner cavity of the valve body (1), a left hydraulic oil inlet (13) and a right hydraulic oil inlet (14) are respectively opened in the left annular groove (11) and the right annular groove (12), a left servo mechanism oil duct (15) and a right servo mechanism oil duct (16) are respectively opened in inner cavities of the valve body on the inner sides of the left annular groove (11) and the right annular groove (12), the left annular groove (11) and the right annular groove (12) are in mirror symmetry about a valve body center line M, the left servo mechanism oil duct (15) and the right servo mechanism oil duct (16) are in mirror symmetry about the valve body center line M, and the widths of the left annular groove (11) and the right annular groove (12) are larger than the diameters of the left servo mechanism oil duct (15) and the servo mechanism right oil duct (16).
4. An improved reversing mechanism for displacement control according to claim 1, wherein: the valve core (2) is provided with a left double-convex ring (21) and a right double-convex ring (22), the left double-convex ring (21) and the right double-convex ring (22) are in mirror symmetry about a valve core central line N, circumferential circular surfaces of the left double-convex ring (21) and the right double-convex ring (22) are in sealing fit with an inner cavity of the valve body (1), and the widths of the left double-convex ring (21) and the right double-convex ring (22) are equal to or slightly larger than the diameters of a left oil duct (15) and a right oil duct (16) of a servo mechanism; the outer sides of the left radial hole (25) and the right radial hole (26) are respectively provided with a left outer convex ring (29) and a right outer convex ring (30), the left outer convex ring (29) and the right outer convex ring (30) are in mirror symmetry with respect to a valve core central line N, the circumferential circular surfaces of the left outer convex ring (29) and the right outer convex ring (30) are in sealing fit with the inner cavity of the valve body (1), the width of a groove between the left outer convex ring (29) and the left double convex ring (21) is larger than that of a left annular groove (11) of the valve body (1), and the width of a groove between the right outer convex ring (30) and the right double convex ring (22) is larger than that of a right annular groove (12) of the valve body (1).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122928646.4U CN216812969U (en) | 2021-11-26 | 2021-11-26 | Improved reversing mechanism for displacement control |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122928646.4U CN216812969U (en) | 2021-11-26 | 2021-11-26 | Improved reversing mechanism for displacement control |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN216812969U true CN216812969U (en) | 2022-06-24 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122928646.4U Active CN216812969U (en) | 2021-11-26 | 2021-11-26 | Improved reversing mechanism for displacement control |
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| Country | Link |
|---|---|
| CN (1) | CN216812969U (en) |
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2021
- 2021-11-26 CN CN202122928646.4U patent/CN216812969U/en active Active
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