Oil supplementing overflow valve

Abstract

The oil supplementing overflow valve comprises a valve seat and a valve element, the oil supplementing overflow valve is provided with a high-pressure side and an oil supplementing side, the valve element penetrates through an inner hole of the valve seat, the valve element and the inner hole of the valve seat are matched to form a first valve port, and the valve element moves towards the oil supplementing side under the action of the pressure of the high-pressure side to open the first valve port; the outer surface of the valve seat is matched with a pump body of the hydraulic pump provided with the oil supplementing overflow valve to form a second valve port, and the valve seat moves towards the high-pressure side under the action of the pressure of the oil supplementing side so as to open the second valve port; wherein a guide concave surface is arranged on the outer surface of the valve seat and at the downstream of the second valve port, and at least one part of the guide concave surface is inclined towards the second valve port along the movement direction of the oil so as to form hydraulic power for driving the valve seat to move along the opening direction. Therefore, under the condition that the pressure difference is certain, the through-flow capacity of the oil supplementing overflow valve can be improved, hysteresis is reduced, the negative effect generated by friction force in the oil supplementing overflow valve can be weakened, and the working effect and stability of the oil supplementing overflow valve are improved.

Description

Technical Field

[0001] This application relates to the technical field of hydraulic systems, and particularly to an oil replenishing overflow valve. Background Art

[0002] The oil replenishing overflow valve is a safety valve for controlling pressure in a hydraulic system. When the system is working normally, the oil replenishing overflow valve is in a closed state. When the system pressure is greater than its set pressure, the overflow function is opened. When the system pressure is less than its set pressure, the oil replenishing function is opened, playing a role in overloading protection and reverse oil replenishment for the system. However, the existing oil replenishing overflow valve has poor flow capacity. When the pressure difference is small, the opening of the valve port is small, and there is an obvious hysteresis phenomenon, thus affecting the effects of overloading protection and reverse oil replenishment. Utility Model Content

[0003] In view of this, this application provides an oil replenishing overflow valve that can improve the flow capacity and reduce the hysteresis.

[0004] To achieve the above object, this application provides the following technical solutions:

[0005] An oil replenishing overflow valve includes a valve seat and a valve core. The oil replenishing overflow valve has a high-pressure side and an oil replenishing side. The valve core passes through the inner hole of the valve seat, and the valve core and the inner hole of the valve seat cooperate to form a first valve port. The valve core moves towards the oil replenishing side under the action of the high-pressure side pressure to open the first valve port; the outer surface of the valve seat cooperates with the pump body of the hydraulic pump on which the oil replenishing overflow valve is installed to form a second valve port. The valve seat moves towards the high-pressure side under the action of the oil replenishing side pressure to open the second valve port;

[0006] Wherein, on the outer surface of the valve seat, downstream of the second valve port, there is a guiding concave surface. Along the movement direction of the oil fluid, at least a part of the guiding concave surface inclines towards the second valve port to form a hydrodynamic force that drives the valve seat to move in the opening direction.

[0007] Optionally, the oil replenishing overflow valve further includes a mounting seat for connecting the pump body. The valve seat and the valve core are both axially elastically displaceably connected to the mounting seat.

[0008] Optionally, the outer surface of the valve seat is provided with:

[0009] A valve port part that cooperates with the pump body to form the second valve port;

[0010] An annular protrusion, which includes an arc chamfer connected to the valve port part and an inclined surface part connected to the arc chamfer. The guiding concave part is composed of the arc chamfer and the inclined surface part.

[0011] Optionally, the valve orifice portion is spherical.

[0012] Optionally, the inclined surface portion is planar or curved.

[0013] Optionally, the included angle formed by the inclined surface portion or the tangent of the outer edge of the inclined surface portion and the radial direction of the valve core is 5-40 degrees.

[0014] Optionally, the included angle formed by the inclined surface portion or the tangent of the outer edge of the inclined surface portion and the radial direction of the valve core is 15-30 degrees.

[0015] Optionally, the side surface of the annular protrusion away from the second valve orifice is provided as a curved surface and is in smooth transition with the guiding concave surface.

[0016] Optionally, the annular protrusion and the valve seat are integrally formed.

[0017] For the oil replenishing overflow valve provided by the present application, the outer surface of the valve seat is provided with an annular protrusion and a valve orifice portion. A guiding concave surface is formed on one side of the annular protrusion close to the valve orifice portion. The guiding concave surface is connected to the valve orifice portion, and at least a part of the guiding concave surface is inclined towards the second valve orifice. When the second valve orifice is opened, the guiding concave surface is downstream of the valve orifice portion. The oil fluid passes through the valve orifice portion and the guiding concave surface in sequence, and under the blocking action of the guiding concave surface, a hydrodynamic force acting on the valve seat is generated. By converting the kinetic energy of the oil fluid flow into the momentum for opening the second valve orifice, a larger opening degree of the second valve orifice can be maintained under a certain pressure difference, thereby improving the flow capacity of the oil replenishing overflow valve and reducing hysteresis. Moreover, due to the increase in the hydrodynamic force, the negative impact caused by the internal friction of the oil replenishing overflow valve can be weakened, and the working effect and stability of the oil replenishing overflow valve can be improved. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only the embodiments of the present application. For those of ordinary skill in the art, other drawings can be obtained according to the provided drawings without creative efforts.

[0019] Figure 1 A three-dimensional view of an oil replenishing overflow valve shown in some embodiments;

[0020] Figure 2 A cross-sectional view of an oil replenishing overflow valve shown in some embodiments;

[0021] Figure 3 A partial cross-sectional view of an oil replenishing overflow valve installed in a pump body shown in some embodiments;

[0022] Figure 4 A cross-sectional view of a valve seat shown in some embodiments.

[0023] In the figure: 1, valve seat; 2, spool; 3, first spring; 4, spring seat; 5, second spring; 6, mounting seat; 7, pump body; 8, working oil port; 9, make-up oil port; 11, valve port part; 12, annular protrusion; 13, guiding concave surface; 14, side hole; 15, first curved surface; 16, second curved surface; 21, head. Specific embodiments

[0024] Next, the technical solutions in the embodiments of the present application will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present application.

[0025] As Figures 1 - 4 shown, the embodiment of the present application provides a make-up overflow valve, including a valve seat 1, a spool 2, a mounting seat 6, a spring seat 4, a first spring 3 and a second spring 5. One end of the mounting seat 6 is open to form a mounting cavity, and the spring seat 4 is slidably arranged in the mounting cavity. The other end of the mounting seat 6 is provided with an external hexagonal structure for easy screwing and installation. The valve seat 1 is provided with an inner hole and side holes 14. The inner hole runs through along the axial direction of the valve seat 1. A plurality of side holes 14 are provided and arranged in a circumferential direction around the valve seat 1. Each side hole 14 communicates with the inner hole in the radial direction.

[0026] The spool 2 has a rod portion and a head 21. The head 21 is arranged at one end of the rod portion. The outer diameter of the head 21 gradually expands in the direction away from the rod portion, so that the outer diameter of the head 21 is greater than the outer diameter of the rod portion. For example, the outer surface of the head 21 is provided as a conical shape or a spherical shape and is integrally formed with the rod portion. Among them, the rod portion of the spool 2 is inserted into the inner hole of the valve seat 1, and a first valve port is formed by cooperating with the inner hole through the head 21. When the outer surface of the head 21 abuts against the inner hole, the first valve port is closed. When the outer surface of the head 21 is separated from the inner hole, the first valve port is opened. The other end of the rod portion of the spool 2 away from the head 21 is connected to the spring seat 4. The first spring 3 is sleeved on the outer periphery of the rod portion. The two ends of the first spring 3 respectively abut against the spring seat 4 and the valve seat 1. The second spring 5 is arranged in the mounting cavity. The two ends of the second spring 5 respectively abut against the spring seat 4 and the bottom of the mounting cavity. Specifically, the second spring 5 is a tower-shaped spring, which has stable centering and a large compression amount. The narrow end of the tower-shaped spring abuts against the spring seat 4, and the wide end abuts against the bottom of the mounting cavity.

[0027] As Figure 3As shown in the figure, this make-up oil overflow valve is installed on the pump body 7 of the hydraulic pump through the mounting seat 6. Specifically, a mounting hole for accommodating the make-up oil overflow valve is provided on the pump body 7, and the mounting seat 6 is connected in the mounting hole through a threaded structure to realize the installation of the make-up oil overflow valve. A working oil port 8 and a make-up oil port 9 are provided in the mounting hole of the pump body 7. After the make-up oil overflow valve is installed, the working oil port 8 is opposite to and communicated with the side hole 14 on the valve seat 1, the make-up oil port 9 is opposite to and communicated with the inner hole on the valve seat 1, and the head 21 of the valve core 2 is located at the position of the make-up oil port 9. In this way, a high-pressure side and a make-up oil side are formed on the make-up oil overflow valve and arranged at intervals in the axial direction. The high-pressure side is the position where the side hole 14 on the valve seat 1 is located, and the make-up oil side is the position where the inner hole on the valve seat 1 cooperates with the head 21 of the valve core 2.

[0028] Among them, at least a part of the outer diameter of the valve seat 1 tapers in the direction away from the spring seat 4, so that the outer surface of the valve seat 1 and the inner wall of the make-up oil port 9 of the pump body 7 cooperate to form a second valve port. When the outer surface of the valve seat 1 abuts against the make-up oil port 9, the second valve port is closed. When the outer surface of the valve seat 1 is separated from the make-up oil port 9, the second valve port is opened.

[0029] During use, when the pressure of the working oil port 8 of the pump body 7 is greater than the pressure of the make-up oil port 9 (that is, the pressure on the high-pressure side is greater than the pressure on the make-up oil side), and the pressure difference exceeds the preset value of the make-up oil overflow valve, the valve core 2 moves along the first axial direction away from the mounting seat 6 (that is, the right direction in Figure 2 ). At this time, the valve seat 1 does not move, and a first valve port is opened between the head 21 of the valve core 2 and the inner hole of the valve seat 1, so that the oil in the working oil port 8 flows through the make-up oil overflow valve to the make-up oil port 9, thereby discharging the high-pressure oil in the working oil port 8 and realizing the overflow function. When the pressure of the working oil port 8 of the pump body 7 is less than the pressure of the make-up oil port 9 (that is, the pressure on the high-pressure side is less than the pressure on the make-up oil side), and the pressure difference exceeds the preset value of the make-up oil overflow valve, the valve seat 1 moves along the second axial direction close to the mounting seat 6 (that is, the left direction in Figure 3 ). At this time, the valve core 2 does not move, and a second valve port formed between the outer peripheral surface of the valve seat 1 and the make-up oil port 9 is opened, so that the oil in the make-up oil port 9 flows through the make-up oil overflow valve to the working oil port 8, thereby increasing the oil pressure of the working oil port 8 and realizing the make-up oil function.

[0030] In this solution, the outer surface of the valve seat 1 is provided with a valve port part 11 and an annular protrusion 12. The outer diameter of the valve port part 11 faces the first axial direction of the mounting seat 6 (that is, Figure 3gradually expands in the left direction (in the figure), and cooperates with the port of the oil replenishing port 9 of the pump body 7 to form a second valve port. Specifically, the shape of the valve port portion 11 can be set as a spherical surface or a conical surface. The annular protrusion 12 protrudes from the outer surface of the valve seat 1 (for example, the annular protrusion 12 is integrally formed with the valve seat 1, which has a stable structure and is convenient for processing), and a guiding concave surface 13 is formed on the side close to the valve port portion 11. The guiding concave surface 13 is connected to the valve port portion 11, and at least a part of the guiding concave surface 13 is inclined towards the second valve port. When the second valve port is opened, the guiding concave surface 13 is downstream of the valve port portion 11, and the oil fluid passes through the valve port portion 11 and the guiding concave surface 13 in sequence, and under the blocking action of the guiding concave surface 13, a hydraulic force acting on the valve seat 1 is generated. By converting the kinetic energy of the oil fluid flow into the momentum for opening the second valve port, a larger opening degree of the second valve port can be maintained under a certain pressure difference, thereby improving the flow capacity of the oil replenishing overflow valve. Moreover, due to the increase in the hydraulic force, the negative impact caused by the internal friction of the oil replenishing overflow valve can be weakened. Specifically, during the opening and closing processes of the second valve port, the directions of the friction forces are opposite, resulting in different spring compression amounts and different through-flow rates of the second valve port under the same pressure difference during the opening and closing processes, that is, there is a hysteresis phenomenon. Due to the increase in the hydraulic force towards the opening direction, the proportion of the friction force in the resultant force is reduced, weakening the hysteresis phenomenon, and the consistency of the flow curves during the opening and closing processes is better. Thus, the working effect and stability of the oil replenishing overflow valve can be improved.

[0031] The guiding concave surface 13 includes an arc chamfer and an inclined surface portion. The arc chamfer is connected between the inclined surface portion and the valve port portion 11. Through the design of arc guiding, a smooth transition is achieved between the inclined surface portion and the valve port portion 11, thereby improving the smoothness of the oil fluid flow, avoiding the accumulation of the oil fluid at the position of the guiding concave surface 13, and reducing the oil fluid congestion.

[0032] As Figure 2 shown, the sectional view of the oil replenishing overflow valve is cut by a plane passing through the axes of the valve core 2 and the valve seat 1. In this sectional view, the valve port portion 11 is in an arc shape, and the arc chamfer is in an arc shape. Particularly, the inclined surface portion can be in a straight line or a curve.

[0033] In the first solution, the inclined surface portion is in a straight line in this sectional view, that is, the shape of the inclined surface portion is a conical surface. During the oil replenishing process, the second valve port remains open, and the oil fluid flows through the valve port portion 11, the arc chamfer, and the inclined surface portion in sequence. Moreover, the straight line formed by the inclined surface portion is inclined with respect to the radial direction of the valve core 2, and the included angle formed therewith is 5 - 40 degrees, preferably 15 - 30 degrees, thereby guiding the oil fluid to the side wall of the working oil port 8 through the inclined surface portion, which is beneficial to forming a better hydraulic force.

[0034] In the second solution, the inclined surface is curved so that the inclined surface is a curved surface, that is, the shape of the inclined surface is a spherical surface or other annular curved surface. During the oil replenishment process, the second valve port remains open, and the oil flows through the valve port part 11, the arc chamfer, and the inclined surface in sequence. Moreover, the tangent of the outer edge of the inclined surface is inclined with respect to the radial direction of the valve core 2, and the included angle formed therewith is 5-40 degrees, preferably 15-30 degrees. Furthermore, the oil can be guided to the side wall of the working oil port 8 through the inclined surface, which is beneficial to forming better hydrodynamic force.

[0035] In addition, it should be noted that in this sectional view, the arc chamfer is an arc, and the inclined surface is a curve (this curve includes an arc), and the above-mentioned curve and arc may coincide or be on the same arc. In combination, the radially outer side surface of the annular protrusion 12 (that is, the side surface of the annular protrusion 12 along the radial direction away from the central axis of the valve seat 1) is a plane, and there is a transition through an arc surface between the annular protrusion 12 and the guiding concave surface 13.

[0036] In addition, as Figure 4 shown, the side of the annular protrusion 12 away from the second valve port is set as the first curved surface 15, and the first curved surface 15 is smoothly transitioned with the guiding concave surface 13. Specifically, the radially outer side surface of the annular protrusion 12 is set as the second curved surface 16, and the connection between the first curved surface 15 and the second curved surface 16 and the connection between the second curved surface 16 and the guiding concave surface 13 are both smoothly transitioned, so that the outer surface of the annular protrusion 12 is smooth and has no sharp corners, which is beneficial to the flow of oil.

[0037] The basic principles of the present application have been described above in combination with specific embodiments. However, it should be pointed out that the advantages, advantages, effects, etc. mentioned in the present application are only examples and not limitations, and it cannot be considered that these advantages, advantages, effects, etc. are essential for each embodiment of the present application. In addition, the above-disclosed specific details are only for the purpose of illustration and easy understanding, rather than limitations. The above details do not limit the present application to necessarily adopt the above specific details to implement.

[0038] The block diagrams of the devices, apparatuses, equipment, and systems involved in the present application are only illustrative examples and do not intend to require or imply that they must be connected, arranged, and configured in the manner shown in the block diagrams. As those skilled in the art will recognize, these devices, apparatuses, equipment, and systems can be connected, arranged, and configured in any way. Words such as "including", "comprising", "having", etc. are open-ended words, meaning "including but not limited to", and can be used interchangeably with them. The word "or" and "and" used here refer to the word "and / or", and can be used interchangeably with it, unless the context clearly indicates otherwise. The word "such as" used here refers to the phrase "such as but not limited to", and can be used interchangeably with it.

[0039] It should be understood that the qualifiers "first", "second", "third", "fourth", "fifth" and "sixth" used in the description of the embodiments of the present application are only for more clearly elaborating the technical solutions and cannot be used to limit the protection scope of the present application.

[0040] The above description has been given for purposes of illustration and description. In addition, this description is not intended to limit the embodiments of the present application to the forms disclosed herein. Although multiple example aspects and embodiments have been discussed above, those skilled in the art will recognize certain variations, modifications, alterations, additions, and sub-combinations thereof.

Claims

1. An oil replenishment relief valve, characterized in that: The invention comprises a valve seat and a valve core, wherein the oil replenishment relief valve has a high-pressure side and an oil replenishment side, the valve core passes through the inner hole of the valve seat, and the valve core cooperates with the inner hole of the valve seat to form a first valve port, and the valve core moves toward the oil replenishment side under the action of the pressure on the high-pressure side to open the first valve port; the outer surface of the valve seat cooperates with the pump body of the hydraulic pump on which the oil replenishment relief valve is installed to form a second valve port, and the valve seat moves toward the high-pressure side under the action of the pressure on the oil replenishment side to open the second valve port; A guide concave surface is provided on the outer surface of the valve seat and downstream of the second valve port. Along the movement direction of the oil, at least a portion of the guide concave surface is inclined toward the second valve port to form a hydraulic force that drives the valve seat to move in the opening direction.

2. The oil replenishment relief valve according to claim 1, characterized in that: The oil replenishment relief valve further comprises a mounting seat, wherein the mounting seat is used to connect with the pump body, and the valve seat and the valve core can be connected to the mounting seat in an axially elastically displaceable manner.

3. The oil replenishment relief valve according to claim 1, characterized in that: The outer surface of the valve seat is provided with: a valve port portion, wherein the valve port portion cooperates with the pump body to form the second valve port; The annular protrusion includes an arc-shaped chamfer connected to the valve mouth portion and an inclined portion connected to the arc-shaped chamfer; the guiding concave surface is composed of the arc-shaped chamfer and the inclined portion.

4. The oil-filling relief valve according to claim 3, characterized in that: The valve mouth portion is spherical.

5. The oil replenishment relief valve according to claim 3, characterized in that: The inclined surface is a plane or a curved surface.

6. The oil-filling relief valve according to claim 5, characterized in that: The angle formed by the inclined surface portion or the tangent line of the outer edge of the inclined surface portion and the radial direction of the valve core is 5-40 degrees.

7. The oil-filling relief valve according to claim 6, characterized in that: The angle formed by the inclined surface portion or the tangent line of the outer edge of the inclined surface portion and the radial direction of the valve core is 15-30 degrees.

8. The oil replenishment relief valve according to claim 3, characterized in that: The side surface of the annular protrusion away from the second valve port is configured as a curved surface and smoothly transitions with the guide concave surface.

9. The oil-filling relief valve according to claim 3, characterized in that: The annular protrusion is integrally formed with the valve seat.

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