Power control valve for axial piston pump and axial piston pump control module

Abstract

The application discloses an axial plunger pump power control valve and an axial plunger pump control module, and belongs to the hydraulic field. The axial plunger pump power control valve comprises an angle feedback assembly, a variable assembly and a valve body assembly. The valve body assembly comprises a valve body shell. The angle feedback assembly is used to be connected with a swash plate of a plunger pump, so as to perceive and transmit the motion state of the swash plate. The variable assembly is arranged on the valve body shell and is connected with the angle feedback assembly. The variable assembly is used to control the flow direction of hydraulic oil according to the motion state of the swash plate, so as to realize the power variable function of the plunger pump. The existing power control valve technology needs to be matched with the structure of a load-sensitive valve to realize the power control function. The axial plunger pump power control valve can realize the power control function of the plunger pump by the structure thereof alone, is compact in structure, is reliable in work, saves the load-sensitive valve while realizing the power control function, and thus reduces the cost.

Description

Technical Field

[0001] This invention belongs to the field of hydraulics and relates to axial piston pump technology, particularly to a power control valve and an axial piston pump control module for axial piston pumps. Background Technology

[0002] Hydraulic equipment almost always requires rapid feeding under low-pressure conditions and slow feeding under high-pressure conditions, which is also the power control characteristic of axial piston pumps. In addition, axial piston pumps with power control functions can fully utilize the power of the prime mover and avoid the prime mover stalling. Therefore, the power control function of axial piston pumps is a necessary control function for almost all hydraulic equipment.

[0003] The power control function of axial piston pumps is mainly achieved through power control valves. However, power control valves often need to be used in conjunction with load-sensitive valves, which not only have a complex structure and large size, but also low reliability and high operating costs. Summary of the Invention

[0004] The purpose of this invention is to provide a power control valve and a control module for an axial piston pump. The power control valve for the axial piston pump realizes the power control function of the piston pump through its own structure. It has a compact structure and reliable operation, which can solve the problems of existing power control valves that need to be used with load-sensitive valves, which are not only complex and bulky, but also have low reliability and high cost.

[0005] To achieve the above objectives, the present invention provides the following solution:

[0006] This invention provides a power control valve for an axial piston pump, comprising:

[0007] Valve body assembly, including valve body housing;

[0008] An angle feedback component is used to connect to the swashplate of the piston pump to sense and transmit the motion state of the swashplate;

[0009] A variable component is disposed on the valve body housing and connected to the angle feedback component. The variable component is used to control the flow direction of hydraulic oil according to the motion state of the swashplate, so as to realize the power variable function of the piston pump.

[0010] Optionally, the angle feedback component is movably embedded within the valve body housing, and the angle feedback component includes:

[0011] A lever, the first end of which is connected to the swashplate;

[0012] A transmission rod, the first end of which is connected to the second end of the lever, and the second end of which is connected to the variable component; the transmission rod is also provided with a feedback pin that is concentrically arranged with the swing center of the swashplate, and the feedback pin is inserted into a corresponding feedback pin hole on the valve body housing to position the transmission rod.

[0013] Optionally, the first end of the lever is provided with a positioning seat, the positioning seat is provided with a lever positioning pin and a mounting hole for screws or bolts to pass through; the second end of the lever is provided with a lever feedback spherical surface.

[0014] The first end of the transmission rod is provided with a U-shaped through hole, which is fitted onto the outside of the feedback spherical surface of the lever; the second end of the transmission rod is provided with a transmission rod feedback spherical surface adapted to the variable component.

[0015] Optionally, the variable component includes:

[0016] A valve core is movably inserted into the valve body housing, and a transmission rod clearance groove is provided on it for the second end of the transmission rod to pass through. The outer wall of the valve core, from the first end to the second end, is provided with three sealing oil steps: a first sealing oil step, a second sealing oil step, and a third sealing oil step. These three steps are all located between the first end of the valve core and the transmission rod clearance groove. The diameters of the second and third sealing oil steps are the same and larger than the diameter of the first sealing oil step. The axial spacing between the first and second sealing oil steps, and between the second and third sealing oil steps, respectively forms oil cavities corresponding to the inner wall of the valve body housing. The valve body is provided with a first control oil passage, a second control oil passage, and a third control oil passage.

[0017] A variable rod is movably inserted into the valve core, and has a through hole that connects to the feedback spherical surface of the transmission rod; the first end of the variable rod extends out of the first end of the valve core and is connected to the variable rod guide plug, and the second end of the variable rod extends out of the second end of the valve core and is connected to the variable rod nut.

[0018] The first spring seat is sleeved on the outer periphery of the variable rod and abuts or connects with the second end of the valve core;

[0019] A first spring is sleeved on the variable rod, and the first end of the first spring abuts against or is connected to the first spring seat;

[0020] The second spring is sleeved outside the first spring, and the first end of the second spring abuts against or is connected to the first spring seat;

[0021] An elastic adjustment mechanism is movably mounted on the second end of the variable rod. The second ends of the first spring and the second spring are both connected to or abut against the elastic adjustment mechanism. The elastic adjustment mechanism can adjust the compression of the first spring and the second spring.

[0022] Optionally, the second end face of the valve core is spherical, which makes spherical contact with the first end face of the first spring seat.

[0023] Optionally, the elasticity adjustment mechanism comprises:

[0024] The second spring seat is movably sleeved on the variable rod and located between the first spring seat and the variable rod nut. The second end of the first spring abuts against or is connected to the second spring seat.

[0025] A first adjusting rod is movably sleeved outside the second spring seat. A first adjusting nut is provided at the end of the first adjusting rod away from the valve core. The second end of the second spring is sleeved outside the first adjusting rod and abuts or connects with the first adjusting nut. A pin is also provided on the inner wall of the first adjusting rod. The first end of the pin abuts or connects with the second spring seat.

[0026] The second adjusting rod is movably sleeved outside the variable rod and located inside the first adjusting rod. The first end of the second adjusting rod abuts against the second end of the pin, and the second end of the second adjusting rod extends outside the second end of the first adjusting rod and is connected to the second adjusting nut.

[0027] Optionally, the valve body housing includes a main housing cover, on which the feedback pin hole and the lever clearance groove are provided. The transmission rod is movably installed inside the main housing cover, and the first end of the lever is located in the lever clearance groove. The main housing cover is provided with a screw plug mounting hole communicating with the feedback pin hole, and a screw plug is installed in the screw plug mounting hole to prevent the feedback pin from coming out of the feedback pin hole. The main housing cover is provided with a valve hole, the valve core is disposed in the valve hole, and the variable rod guide plug is disposed at one end of the valve hole. The first control oil passage, the second control oil passage, and the third control oil passage are all disposed on the main housing cover.

[0028] Optionally, the valve body housing further includes a variable component housing, which is sealed to the other end of the valve port to enclose the first spring seat, the first spring, the second spring, and the elastic adjustment mechanism of the variable component.

[0029] Optionally, the main body housing may also be provided with at least one of a metal sealing gasket, a mounting positioning pin, and a fixing screw.

[0030] This invention also proposes an axial piston pump control module, including an axial piston pump and a power control valve for the axial piston pump as described above. The axial piston pump includes a swashplate, with a large variable piston connected to one side and a small variable piston connected to the other side. A small variable piston spring is sleeved on the outside of the small variable piston. The first end of the lever is connected to the swashplate. The first control oil passage is connected to the high-pressure oil outlet of the axial piston pump. The second control oil passage is connected to the large piston chamber of the large variable piston. The third control oil passage is connected to the housing chamber of the axial piston pump.

[0031] The present invention achieves the following technical effects compared to the prior art:

[0032] This invention discloses a power control valve for an axial piston pump, comprising an angle feedback component, a variable component, and a valve body assembly. The valve body assembly includes a valve body housing. The angle feedback component is connected to the swashplate of the piston pump to sense and transmit the swashplate's motion state. The variable component is disposed on the valve body housing and connected to the angle feedback component. The variable component controls the flow direction of hydraulic oil according to the swashplate's motion state to achieve the power variable function of the piston pump. Existing power control valve technology requires the use of a load-sensitive valve to achieve power control. However, the power control valve for the axial piston pump of this invention can achieve the power control function of the piston pump independently through its own structure. It is compact, reliable, and eliminates the need for a load-sensitive valve while achieving power control, thereby reducing costs. This is crucial for hydraulic equipment, especially hydraulic equipment in engineering machinery.

[0033] The axial piston pump control module disclosed in this invention includes an axial piston pump and a power control valve for an axial piston pump as described above, and has all the features of a power control valve for an axial piston pump, which will not be repeated here. Attached Figure Description

[0034] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0035] Figure 1 This is a schematic diagram of the overall structure of the power control valve for an axial piston pump disclosed in an embodiment of the present invention;

[0036] Figure 2 This is a schematic diagram of the axial piston pump control module disclosed in an embodiment of the present invention;

[0037] Figure 3This is a schematic diagram of the angle feedback component of the power control valve for the axial piston pump disclosed in an embodiment of the present invention;

[0038] Figure 4 This is a schematic diagram of the variable component of the power control valve for an axial piston pump disclosed in an embodiment of the present invention;

[0039] Figure 5 This is a schematic diagram of the valve body assembly of the power control valve for an axial piston pump disclosed in an embodiment of the present invention;

[0040] Figure 6 This is a schematic diagram of the lever structure in the angle feedback component disclosed in an embodiment of the present invention;

[0041] Figure 7 This is a schematic diagram of the transmission rod in the angle feedback component disclosed in an embodiment of the present invention;

[0042] Figure 8 This is a schematic diagram of the valve core structure in the variable component disclosed in an embodiment of the present invention;

[0043] Figure 9 This is a schematic diagram of the variable rod structure in the variable assembly disclosed in an embodiment of the present invention;

[0044] Figure 10 This is a first-view structural diagram of the first spring seat in the variable component disclosed in an embodiment of the present invention;

[0045] Figure 11 This is a schematic diagram of the second-view structure of the first spring seat in the variable component disclosed in an embodiment of the present invention;

[0046] Figure 12 This is a first-view structural diagram of the second spring seat in the variable component disclosed in an embodiment of the present invention;

[0047] Figure 13 This is a schematic diagram of the second view structure of the second spring seat in the variable component disclosed in an embodiment of the present invention;

[0048] Figure 14 This is a schematic diagram of the first perspective structure of the first adjusting rod in the variable component disclosed in an embodiment of the present invention;

[0049] Figure 15 This is a schematic diagram of the second perspective structure of the first adjusting rod in the variable component disclosed in an embodiment of the present invention;

[0050] Figure 16 This is a schematic diagram of the structure of the ejector pin in the variable component disclosed in an embodiment of the present invention;

[0051] Figure 17 This is a schematic diagram of the first-view structure of the second adjusting rod in the variable component disclosed in an embodiment of the present invention;

[0052] Figure 18 This is a schematic diagram of the second perspective structure of the second adjusting rod in the variable component disclosed in an embodiment of the present invention;

[0053] Figure 19 This is a schematic diagram of the variable rod guide plug in the variable assembly disclosed in an embodiment of the present invention;

[0054] Figure 20 This is a first-view structural diagram of the main body cover in the valve body assembly disclosed in an embodiment of the present invention;

[0055] Figure 21 This is a second-view structural diagram of the main housing in the valve body assembly disclosed in an embodiment of the present invention.

[0056] The attached figures are labeled as follows: 1. Power control valve for axial piston pump; 2. Swashplate; 3. Large variable piston; 4.1. Small variable piston; 4.2. Small variable piston spring; 5. Pulley; 501. Locating pin hole; 502. Mounting hole; 503. Pulley feedback spherical surface; 6. Pulley locating pin; 7. Pulley fixing screw; 8. Drive rod; 801. U-shaped through hole; 802. Drive rod feedback spherical surface; 803. Feedback pin mounting hole; 9. Feedback pin; 10. Valve core; 1001. Drive rod clearance groove; 1002. Oil sealing platform. Step 1; 1003, Oil sealing step 2; 1004, Oil sealing step 3; 1005, First through hole; 1006, First spherical surface; 11, Variable rod; 1101, Second through hole; 1102, Stud; 1103, Guide surface; 12, Variable rod guide plug; 1201, Guide hole; 13, Variable rod nut; 14, Second adjusting rod; 1401, Clearance groove; 1402, External thread; 1403, Ejector pin support surface; 1404, Hexagonal hole; 15, First adjusting rod; 1501, External thread; 1502, Internal thread 1503, Ejector pin clearance hole; 1504, Third through hole; 1505, Limiting surface; 1506, Hexagonal surface; 1507, First spring seat clearance hole; 16, Second spring seat; 1601, Second spring support surface; 1602, Ejector pin support surface; 1603, Clearance hole; 17, First spring seat; 1701, Second spherical surface; 1702, First spring support surface; 1703, Third spring support surface; 18, First spring; 19, Second spring; 20, Ejector pin; 2001, Circular boss; 21, Second 22. Adjusting rod locking nut; 23. First adjusting nut; 23. Valve body housing; 2301. Feedback pin hole; 2302. Lever clearance groove; 2303. Valve hole; 2304. Control oil passage one; 2305. Control oil passage two; 2306. Control oil passage three; 2307. Screw plug mounting hole; 2308. Variable assembly housing mounting hole; 2309. Variable rod guide plug mounting hole; 24. Fixing screw; 25. Mounting positioning pin; 26. Metal sealing gasket; 27. Screw plug; 28. Variable assembly housing; 29. ​​Main body housing. Detailed Implementation

[0057] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0058] One of the objectives of this invention is to provide a power control valve for an axial piston pump, which achieves the power control function of the piston pump through its own structure. It has a compact structure and reliable operation, and can solve the problems of existing power control valves that need to be used with load-sensitive valves, which are not only complex and bulky, but also have low reliability and high operating costs.

[0059] Another object of the present invention is to provide an axial piston pump control module having the power control valve for the axial piston pump described above.

[0060] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0061] Example 1

[0062] like Figure 1 and Figure 2 As shown, this embodiment provides a power control valve 1 for an axial piston pump, including a valve body assembly, an angle feedback assembly, and a variable displacement assembly. The valve body assembly includes a valve body housing 23, which is mainly used for mounting the control valve on the piston pump. The angle feedback assembly is connected to the swashplate 2 of the piston pump to sense and transmit the motion state of the swashplate 2. The variable displacement assembly is disposed on the valve body housing 23 and connected to the angle feedback assembly. The variable displacement assembly is used to control the flow direction of hydraulic oil according to the motion state of the swashplate 2, thereby realizing the power variable displacement function of the piston pump.

[0063] In this embodiment, the angle feedback component is movably embedded in the valve body housing 23. The angle feedback component includes a lever 5 and a transmission rod 8. The first end of the lever 5 is connected to the swashplate 2, the first end of the transmission rod is connected to the second end of the lever 5, and the second end of the transmission rod 8 is connected to the variable component. The transmission rod 8 is also provided with a feedback pin 9 that is concentrically arranged with the swing center of the swashplate 2. The feedback pin 9 is inserted into the corresponding feedback pin hole 2301 on the valve body housing 23 to position the transmission rod 8.

[0064] In this embodiment, a positioning seat is provided at the first end of the lever 5, and the positioning seat is provided with a lever positioning pin 6 and a mounting hole 502, such as Figure 3 and Figure 6As shown, each end of the positioning seat has a positioning pin hole 501, and a lever positioning pin 6 is inserted into each positioning pin hole 501. The lever 5 is positioned with the swashplate 2 of the plunger pump through the two lever positioning pins 6. The mounting hole 502 is located between the two lever positioning pins 6 and is used for the lever fixing screw 7 to pass through, so that the first end of the lever 5 is fixed to the swashplate 2 by the lever fixing screw 7. The second end of the lever 5 is provided with a lever feedback spherical surface 503; the first end of the transmission rod 8 is provided with a U-shaped through hole 801, which is fitted onto the outside of the lever feedback spherical surface 503; the second end of the transmission rod 8 is provided with a transmission rod feedback spherical surface 802 adapted to the variable component. Figure 3 and Figure 6 As shown, a feedback pin mounting hole 803 is provided in the middle part (not necessarily the midpoint) of the transmission rod 8 for inserting the feedback pin 9.

[0065] In this embodiment, the variable component includes a valve core 10, a variable rod 11, a first spring seat 17, a first spring 18, a second spring 19, and a spring force adjustment mechanism. A valve hole 2303 is provided inside the main body housing 29, arranged axially. The valve core 10 is movably inserted into the valve hole 2303 of the main body housing 29. A transmission rod clearance groove 1001 is provided on the valve core 10 for the second end of the transmission rod 8 to pass through. The outer wall of the valve core 10, from the first end to the second end, is provided with a sealing step 1002, a sealing step 2003, and a sealing step 3004. These sealing steps are located at the first end of the valve core 10 and the transmission rod clearance groove. Between 1001, the diameters of sealing oil step two 1003 and sealing oil step three 1004 are the same and larger than the diameter of sealing oil step one 1002. The axial spacing between sealing oil step one 1002 and sealing oil step two 1003, and the axial spacing between sealing oil step two 1003 and sealing oil step three 1004, respectively form oil cavities corresponding to the inner wall of the valve body shell 23. The valve body shell 23 is provided with control oil passage one 2304, control oil passage two 2305, and control oil passage three 2306. The three oil passages of control oil passage one 2304, control oil passage two 2305, and control oil passage three 2306 cooperate with the movement position of the valve core 10 to control the flow direction of oil. The aforementioned sealing oil step one 1002... Oil sealing steps 1003 and 1004 are used to isolate the control oil of the three control oil passages (i.e., control oil passage 1 2304, control oil passage 2 2305, and control oil passage 3 2306) and generate hydraulic thrust on the valve core due to the difference in step area; the variable rod 11 is movably inserted into the valve core 10, and the variable rod 11 has a second through hole 1101 that is inserted into the feedback ball surface 802 of the transmission rod. The second through hole 1101 and the feedback ball surface 802 of the transmission rod are used together to achieve the purpose of transmitting the position of the swashplate; the first end of the variable rod 11 extends out of the first end of the valve core 10, and the first end of the variable rod 11 is provided with a guide surface 1103 and connected to the variable rod guide plug 12. The guide surface 1103 and the variable rod guide plug 12 are connected to the valve core 10. The guide plug 12 is used in conjunction to guide the variable rod 11. The second end of the variable rod 11 extends beyond the second end of the valve core 10, and a stud 1102 is provided at the second end of the variable rod 11, which is connected to the variable rod nut 13, thus constraining the position of the variable rod 11 and the first adjusting rod 15. The first spring seat 17 is sleeved on the outer periphery of the variable rod 11 and abuts or connects with the second end of the valve core 10. The first spring 18 is sleeved on the variable rod 11, and the first end of the first spring 18 abuts or connects with the first spring seat 17. The diameter of the second spring 19 is larger than that of the first spring 18, and it is sleeved outside the first spring 18, and the first end of the second spring 19 abuts or connects with the first spring seat 17.The elastic adjustment mechanism is movably mounted on the second end of the variable rod 11. The second ends of both the first spring 18 and the second spring 19 are connected to or abut against the elastic adjustment mechanism, which can adjust the compression of the first spring 18 and the second spring 19.

[0066] Furthermore, such as Figure 4 As shown, the second end face of the valve core 10 is a first spherical surface 1006, which contacts and engages with the second spherical surface 1701 of the first end face of the first spring seat 17. The first spherical surface 1006 and the second spherical surface 1701 work together to provide centering, ensuring that the spring force acting on the first spring seat 17 is transmitted axially along the valve core 10, preventing the valve core from generating lateral force that could cause it to jam. The first spring seat 17 is provided with a first spring support surface 1702 and a third spring support surface 1703, which are used to support the second spring 19 and the first spring 18, respectively. The second spring 19 is a high-power spring, and the first spring 18 is a low-power spring.

[0067] In this embodiment, the elastic adjustment mechanism includes a second spring seat 16, a first adjusting rod 15, and a second adjusting rod 14. The second spring seat 16 is movably sleeved on the variable rod 11 and located between the first spring seat 17 and the variable rod nut 13. The second end of the first spring 18 abuts against or is connected to the second spring seat 16. The first adjusting rod 15 is movably sleeved outside the second spring seat 16. A first adjusting nut 22 is provided at the end of the first adjusting rod 15 away from the valve core 10. The second end of the second spring 19 is sleeved outside the first adjusting rod 15 and abuts against or is connected to the first adjusting nut 22. A pin 20 is also provided on the inner wall of the first adjusting rod 15. The first end of the pin 20 abuts against or is connected to the second spring seat 16. The second adjusting rod 14 is movably sleeved outside the variable rod 11 and located inside the first adjusting rod 15. The first end of the second adjusting rod 14 abuts against the second end of the pin 20. The second end of the second adjusting rod 14 extends outside the second end of the first adjusting rod 15 and is connected to the second adjusting nut, i.e., the second adjusting rod locking nut 21.

[0068] In this embodiment, the second spring seat 16 is provided with a second spring support surface 1601 and a ejector pin support surface 1602. The second spring support surface 1601 is used to support the first spring 18, and the ejector pin support surface 1602 is used to support the ejector pin 20 and thus transmit the adjustment force from the ejector pin 20. The second spring seat 16 is provided with a clearance hole 1603 for passing through the variable rod 11.

[0069] Furthermore, the first adjusting rod 15 is provided with an external thread 1501 for installing a first adjusting nut 22, thereby adjusting the second spring 19 by tightening the first adjusting nut 22. The first adjusting rod 15 is provided with an internal thread 1502 for installing a second adjusting rod 14, thereby adjusting the first spring 18 by tightening the second adjusting rod 14. The first adjusting rod 15 is provided with three ejector pin clearance holes 1503 for passing through ejector pins 20, thereby transmitting the displacement of the second adjusting rod 14 to the second spring seat 16 through the ejector pins. The first adjusting rod 15 is provided with a third through hole 1504 for passing through the variable rod 11. The first adjusting rod 15 is also provided with a limiting surface 1505, which cooperates with the variable rod nut 13 to prevent the first adjusting rod 15 from sliding out of the variable rod 11 under the action of the second spring 19. A hexagonal face 1506 is provided at the external thread 1501 of the first adjusting rod 15 for securing it when tightening the first adjusting nut 22, the second adjusting rod locking nut 21, and the second adjusting rod 14. The first adjusting rod 15 is provided with a first spring seat clearance hole 1507 to avoid the second spring seat 16.

[0070] Furthermore, a circular boss 2001 is provided at the end of the ejector pin 20. The circular boss 2001 can prevent the ejector pin 20 from slipping out of the first spring seat clearance hole 1507 and affecting the adjustment of the first spring 18.

[0071] In this embodiment, the second adjusting rod 14 is provided with a clearance groove 1401 to avoid the variable rod nut 13; the second adjusting rod 14 is provided with an external thread 1402 to cooperate with the internal thread 1502 of the first adjusting rod 15; the second adjusting rod 14 is provided with a pin support surface 1403 to cooperate with the pin 20; and the end of the second adjusting rod 14 is provided with a hexagonal hole 1404 for adjustment with an internal hex wrench.

[0072] In this embodiment, a guide hole 1201 is provided on the variable rod guide plug 12 for guiding the variable rod 11.

[0073] In this embodiment, the valve body housing 23 includes a main housing cover 29. The main housing cover 29 has a feedback pin hole 2301 and a lever clearance groove 2302. The transmission rod 8 is movably installed inside the main housing cover 29. The feedback pin hole 2301 is used to position the transmission rod 8, and the lever clearance groove 2302 is used to avoid the lever 5. The main housing cover 29 is provided with a screw plug mounting hole 2307 communicating with the feedback pin hole 2301. The screw plug mounting hole 2307 is the feedback pin hole 2301. 301 provides installation space, and a screw plug 27 (i.e., screw plug) is installed in the screw plug mounting hole 2307 to prevent the feedback pin 9 from coming out of the feedback pin hole 2301; a valve hole 2303 is provided on the main body cover 29, the valve core 10 is provided in the valve hole 2303, and the variable rod guide plug 12 is provided at one end of the valve hole 2303; control oil passage one 2304, control oil passage two 2305 and control oil passage three 2306 are all provided on the main body cover 29.

[0074] In this embodiment, the valve body housing 23 further includes a variable component housing 28, which is sealed and connected to the other end of the valve port 2303 to enclose the first spring seat 17, the first spring 18, the second spring 19, and the aforementioned elastic adjustment mechanism of the variable component. Figure 20 and Figure 21 As shown, the main housing 29 is provided with a variable component housing mounting hole 2308 for mounting the variable component housing 28, and the main housing 29 is also provided with a variable rod guide plug mounting hole 2309 for mounting the variable rod guide plug 12. The variable component housing mounting hole 2308 and the variable rod guide plug mounting hole 2309 are preferably coaxially arranged.

[0075] In this embodiment, the main housing 29 is further provided with at least one of a metal sealing gasket 26, a mounting positioning pin 25, and a fixing screw 24. As a preferred embodiment, the main housing 29 is provided with a metal sealing gasket 26, a mounting positioning pin 25, and a fixing screw 24 simultaneously, as detailed below. Figure 5 , Figure 20 and Figure 21 As shown.

[0076] The working principle of the power control valve 1 for the axial piston pump described in this embodiment will be explained in detail below.

[0077] The swing angle of the swashplate 2, which corresponds to the displacement of the plunger pump, is transmitted to the variable rod 11 via the lever 5 and the transmission rod 8. The lever 5 is positioned on the swashplate 2 through two locating pin holes 501 and fixed to the swashplate 2 by the lever fixing screw 7. The lever feedback spherical surface 503 at the top of the lever 5 is tangentially contacted with the U-shaped through hole 801 of the transmission rod 8 to achieve actuation. The feedback spherical surface 802 of the transmission rod is tangentially contacted with the second through hole 1101 of the variable rod 11 to achieve actuation. A feedback pin mounting hole 803 is provided in the middle of the transmission rod 8, which serves as the rotation center of the transmission rod 8 and is concentric with the rotation center of the swashplate 2. In operation:

[0078] Hydraulic oil from control oil passage 2304 generates a hydraulic thrust on valve core 10 in the oil chamber formed by sealing step 1002 and sealing step 1003. This hydraulic thrust and the spring force generated on valve core 10 by the first spring seat 17 form a pair of forces. If the hydraulic thrust is greater than the spring force (the sum of the elastic forces of the first spring 18 and the second spring 19), the valve core 10 moves towards the spring side, causing control oil passage 1 2304 and control oil passage 2 2305 to connect. Since control oil passage 1 2304 is connected to the high-pressure oil outlet of the plunger pump, and control oil passage 2 2305 is connected to the large piston chamber of the large variable piston 3, hydraulic oil enters the large piston chamber and generates hydraulic thrust to push the large variable piston 3 to move. The large variable piston 3 pushes the swashplate 2 to swing, making the swing angle of the swashplate 2 smaller, that is, the displacement of the plunger pump smaller. The smaller swing angle of the swashplate 2 drives the lever 5, the transmission rod 8 and the variable rod 11 to move. The movement of the variable rod 11 drives the first adjusting rod 15 to move, causing the second spring 19 and the first spring 18 to be compressed, increasing the force acting on the valve core 10 until the hydraulic pressure and spring force on the valve core 10 are equal. At this time, the valve core 10 maintains dynamic balance at the position of control oil passage 2 2305, and the plunger pump works at the corresponding displacement. If the hydraulic thrust is less than the spring force (the sum of the spring forces of the first spring 18 and the second spring 19), the valve core 10 moves towards the variable rod guide plug 12, causing control oil passage 2305 and control oil passage 3306 to connect. Control oil passage 3306 connects to the piston pump housing cavity. At this time, the hydraulic oil in the large piston cavity of the large variable piston 3 enters the piston pump housing cavity through control oil passage 3306, achieving the purpose of pressure relief. At this time, the hydraulic thrust of the hydraulic oil on the large variable piston 3 disappears. Due to the small variable piston spring 4.2 on the small variable piston... 4.1 The spring thrust is always generated, so the swing angle of the swashplate 2 increases under the action of the small variable piston 4.1, that is, the displacement of the plunger pump increases. The increased swing angle of the swashplate 2 drives the lever 5, the transmission rod 8 and the variable rod 11 to move. The movement of the variable rod 11 drives the first adjusting rod 15 to move, which causes the compression of the second spring 19 and the first spring 18 to decrease, and the spring force generated to decrease until the hydraulic pressure and spring force on the valve core 10 are equal. At this time, the valve core maintains dynamic balance at the position of the control oil passage 2305, and the plunger pump works at the corresponding displacement.

[0079] When setting the power, the first adjusting nut 22 and the second adjusting rod 14 need to be turned. Turning the first adjusting nut 22 and the second adjusting rod 14 in increases the spring force (the sum of the elastic forces of the first spring 18 and the second spring 19) acting on the valve core 10, and the corresponding power value increases. Turning the first adjusting nut 22 and the second adjusting rod 14 out decreases the spring force (the sum of the elastic forces of the first spring 18 and the second spring 19) acting on the valve core 10, and the corresponding power value decreases.

[0080] Therefore, it can be seen that the power control valve for axial piston pumps proposed in this technical solution can realize the power control function of piston pumps by its own structure. It is compact in structure and reliable in operation. While realizing the power control function, it eliminates the need for a load-sensitive valve, thereby reducing costs. This is crucial for hydraulic equipment, especially hydraulic equipment for engineering machinery.

[0081] Example 2

[0082] This embodiment also proposes an axial piston pump control module, including an axial piston pump and a power control valve 1 for the axial piston pump as described in Embodiment 1. The axial piston pump includes a swashplate 2, with a large variable piston 3 connected to one side and a small variable piston 4.1 connected to the other side. A small variable piston spring 4.2 is fitted around the outside of the small variable piston 4.1. The first end of a lever 5 is connected to the swashplate 2. Control oil passage 1 2304 communicates with the high-pressure oil outlet of the axial piston pump, control oil passage 2 communicates with the large piston chamber of the large variable piston 3, and control oil passage 3 2306 communicates with the housing chamber of the axial piston pump. The aforementioned swashplate 2, large variable piston 3, small variable piston 4.1, and small variable piston spring 4.2 are conventional components of an axial piston pump, and will not be described in detail here.

[0083] The swing angle of the swashplate 2, which corresponds to the displacement of the plunger pump, is transmitted to the variable rod 11 via the lever 5 and the transmission rod 8. The lever 5 is positioned on the swashplate 2 through two locating pin holes 501 and fixed to the swashplate 2 by the lever fixing screw 7. The lever feedback spherical surface 503 at the top of the lever 5 is tangentially contacted with the U-shaped through hole 801 of the transmission rod 8 to achieve actuation. The feedback spherical surface 802 of the transmission rod is tangentially contacted with the second through hole 1101 of the variable rod 11 to achieve actuation. A feedback pin mounting hole 803 is provided in the middle of the transmission rod 8, which serves as the rotation center of the transmission rod 8 and is concentric with the rotation center of the swashplate 2. In operation:

[0084] Hydraulic oil from control oil passage 2304 generates a hydraulic thrust on valve core 10 in the oil chamber formed by sealing step 1002 and sealing step 1003. This hydraulic thrust and the spring force generated on valve core 10 by the first spring seat 17 form a pair of forces. If the hydraulic thrust is greater than the spring force (the sum of the elastic forces of the first spring 18 and the second spring 19), the valve core 10 moves towards the spring side, causing control oil passage 1 2304 and control oil passage 2 2305 to connect. Since control oil passage 1 2304 is connected to the high-pressure oil outlet of the plunger pump, and control oil passage 2 2305 is connected to the large piston chamber of the large variable piston 3, hydraulic oil enters the large piston chamber and generates hydraulic thrust to push the large variable piston 3 to move. The large variable piston 3 pushes the swashplate 2 to swing, making the swing angle of the swashplate 2 smaller, that is, the displacement of the plunger pump smaller. The smaller swing angle of the swashplate 2 drives the lever 5, the transmission rod 8 and the variable rod 11 to move. The movement of the variable rod 11 drives the first adjusting rod 15 to move, causing the second spring 19 and the first spring 18 to be compressed, increasing the force acting on the valve core 10 until the hydraulic pressure and spring force on the valve core 10 are equal. At this time, the valve core 10 maintains dynamic balance at the position of control oil passage 2 2305, and the plunger pump works at the corresponding displacement. If the hydraulic thrust is less than the spring force (the sum of the spring forces of the first spring 18 and the second spring 19), the valve core 10 moves towards the variable rod guide plug 12, causing control oil passage 2305 and control oil passage 3306 to connect. Control oil passage 3306 connects to the piston pump housing cavity. At this time, the hydraulic oil in the large piston cavity of the large variable piston 3 enters the piston pump housing cavity through control oil passage 3306, achieving the purpose of pressure relief. At this time, the hydraulic thrust of the hydraulic oil on the large variable piston 3 disappears. Due to the small variable piston spring 4.2 on the small variable piston... 4.1 The spring thrust is always generated, so the swing angle of the swashplate 2 increases under the action of the small variable piston 4.1, that is, the displacement of the plunger pump increases. The increased swing angle of the swashplate 2 drives the lever 5, the transmission rod 8 and the variable rod 11 to move. The movement of the variable rod 11 drives the first adjusting rod 15 to move, which causes the compression of the second spring 19 and the first spring 18 to decrease, and the spring force generated to decrease until the hydraulic pressure and spring force on the valve core 10 are equal. At this time, the valve core maintains dynamic balance at the position of the control oil passage 2305, and the plunger pump works at the corresponding displacement.

[0085] When setting the power, the first adjusting nut 22 and the second adjusting rod 14 need to be turned. Turning the first adjusting nut 22 and the second adjusting rod 14 in increases the spring force (the sum of the elastic forces of the first spring 18 and the second spring 19) acting on the valve core 10, and the corresponding power value increases. Turning the first adjusting nut 22 and the second adjusting rod 14 out decreases the spring force (the sum of the elastic forces of the first spring 18 and the second spring 19) acting on the valve core 10, and the corresponding power value decreases.

[0086] Therefore, it can be seen that the axial piston pump control module proposed in this technical solution uses an axial piston pump power control valve that can realize the power control function of the piston pump by its own structure. It has a compact structure, reliable operation, and eliminates the need for a load-sensitive valve while realizing the power control function, thereby reducing costs and making it highly practical.

[0087] It should be noted that, for those skilled in the art, it is obvious that the present invention is not limited to the details of the above exemplary embodiments, and that the present invention can be implemented in other specific forms without departing from the spirit or essential characteristics of the invention. Therefore, the embodiments should be considered exemplary and non-limiting in all respects, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention, and no reference numerals in the claims should be construed as limiting the scope of the claims.

[0088] Specific examples have been used to illustrate the principles and implementation methods of this invention. The descriptions of the above embodiments are only for the purpose of helping to understand the method and core ideas of this invention. Furthermore, those skilled in the art will recognize that, based on the ideas of this invention, there will be changes in the specific implementation methods and application scope. Therefore, the content of this specification should not be construed as a limitation of this invention.

Claims

1. A power control valve for an axial piston pump, characterized in that, include: Valve body assembly, including valve body housing; An angle feedback component is used to connect to the swashplate of the piston pump to sense and transmit the motion state of the swashplate; The angle feedback component is movably embedded within the valve body housing. The angle feedback component includes a lever and a transmission rod. The first end of the lever is connected to the swashplate. The first end of the lever has a positioning seat with a lever positioning pin and a mounting hole for screws or bolts to pass through. The second end of the lever has a lever feedback spherical surface. The first end of the transmission rod is connected to the second end of the lever and has a U-shaped through hole that fits over the lever feedback spherical surface. The second end of the transmission rod is connected to a variable component and has a transmission rod feedback spherical surface adapted to the variable component. The transmission rod also has a feedback pin concentrically positioned with the swashplate's swing center. This feedback pin is inserted into a corresponding feedback pin hole on the valve body housing to position the transmission rod. A variable displacement assembly, disposed on the valve body housing and connected to the angle feedback assembly, is used to control the flow direction of hydraulic oil according to the motion state of the swashplate, thereby realizing the power variable function of the piston pump. The variable displacement assembly includes a valve core, a variable displacement rod, a first spring seat, a first spring, a second spring, and a spring force adjustment mechanism. The valve core is movably inserted into the valve body housing and has a transmission rod clearance groove for the second end of the transmission rod to pass through. The outer wall of the valve core, from the first end to the second end, is provided with three sealing steps: a first sealing step, a second sealing step, and a third sealing step. These three steps are located between the first end of the valve core and the transmission rod clearance groove. The diameters of the second and third sealing steps are the same and larger than the diameter of the first sealing step. The axial spacing between the first and second sealing steps, and between the second and third sealing steps, corresponds to the inner wall of the valve body housing. The valve body is provided with an oil cavity, and control oil passages one, two, and three are provided on the valve body. The variable rod is movably inserted into the valve core, and has a through hole for insertion with the feedback spherical surface of the transmission rod. The first end of the variable rod extends out of the first end of the valve core and is connected to the variable rod guide plug. The second end of the variable rod extends out of the second end of the valve core and is connected to the variable rod nut. The first spring seat is sleeved on the outer periphery of the variable rod and abuts or connects with the second end of the valve core. The first spring is sleeved on the variable rod, and the first end of the first spring abuts or connects with the first spring seat. The second spring is sleeved on the outside of the first spring, and the first end of the second spring abuts or connects with the first spring seat. The elastic adjustment mechanism is movably installed on the second end of the variable rod. The second ends of the first spring and the second spring are both connected to or abut against the elastic adjustment mechanism. The elastic adjustment mechanism can adjust the compression of the first spring and the second spring.

2. The power control valve for an axial piston pump according to claim 1, characterized in that, The second end face of the valve core is spherical, which makes spherical contact with the first end face of the first spring seat.

3. The power control valve for an axial piston pump according to claim 1 or 2, characterized in that, The elasticity adjustment mechanism includes: The second spring seat is movably sleeved on the variable rod and located between the first spring seat and the variable rod nut. The second end of the first spring abuts against or is connected to the second spring seat. A first adjusting rod is movably sleeved outside the second spring seat. A first adjusting nut is provided at the end of the first adjusting rod away from the valve core. The second end of the second spring is sleeved outside the first adjusting rod and abuts or connects with the first adjusting nut. A pin is also provided on the inner wall of the first adjusting rod. The first end of the pin abuts or connects with the second spring seat. The second adjusting rod is movably sleeved outside the variable rod and located inside the first adjusting rod. The first end of the second adjusting rod abuts against the second end of the pin, and the second end of the second adjusting rod extends outside the second end of the first adjusting rod and is connected to the second adjusting nut.

4. The power control valve for an axial piston pump according to claim 3, characterized in that, The valve body housing includes a main housing cover, on which the feedback pin hole and the lever clearance groove are provided. The transmission rod is movably installed inside the main housing cover, and the first end of the lever is located in the lever clearance groove. The main housing cover is provided with a screw plug mounting hole communicating with the feedback pin hole. A screw plug is installed in the screw plug mounting hole to prevent the feedback pin from coming out of the feedback pin hole. The main housing cover is provided with a valve hole, in which the valve core is disposed. The variable rod guide plug is disposed at one end of the valve hole. Control oil passage one, control oil passage two, and control oil passage three are all disposed on the main housing cover.

5. The power control valve for an axial piston pump according to claim 4, characterized in that, The valve body housing also includes a variable component housing, which is sealed and connected to the other end of the valve hole to enclose the first spring seat, the first spring, the second spring, and the elastic adjustment mechanism of the variable component.

6. The power control valve for an axial piston pump according to claim 4, characterized in that, The main body shell is also provided with at least one of the following: a metal sealing gasket, a mounting positioning pin, and a fixing screw.

7. An axial piston pump control module, characterized in that, The invention includes an axial piston pump and a power control valve for the axial piston pump as described in any one of claims 1 to 6. The axial piston pump includes a swashplate, a large variable piston connected to one side of the swashplate and a small variable piston connected to the other side, and a small variable piston spring sleeved on the outside of the small variable piston. The first end of the lever is connected to the swashplate, the first control oil passage is connected to the high-pressure oil outlet of the axial piston pump, the second control oil passage is connected to the large piston chamber of the large variable piston, and the third control oil passage is connected to the housing chamber of the axial piston pump.

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