CN119593984A

CN119593984A - Integrated adjustable pump

Info

Publication number: CN119593984A
Application number: CN202411790082.4A
Authority: CN
Inventors: 郭强; 唐文魁; 熊尚明; 李定华
Original assignee: Changsha Kaimai Xinneng Technology Co ltd
Current assignee: Changsha Kaimai Xinneng Technology Co ltd
Priority date: 2024-12-06
Filing date: 2024-12-06
Publication date: 2025-03-11

Abstract

The invention discloses an integrated adjustable pump which comprises a pump body, an oil distribution assembly, a driving assembly and an executing mechanism. The oil distribution assembly comprises a sloping cam plate, a ball head support, a plurality of ball head connecting rods and a plurality of plungers, wherein two ends of the ball head connecting rods are respectively hinged with the sloping cam plate and the corresponding plungers. The driving assembly comprises a driving shaft, a limiting disc, an inclination disc and a plurality of guide posts, wherein the driving shaft is fixedly connected with the limiting disc, one end of each guide post is in spherical hinge connection with the corresponding inclination disc, and the other end of each guide post movably penetrates through the corresponding limiting disc and then is in contact with the swash plate. The actuator is used to drive the tilt disc in rotation to change the tilt angle relative to the drive shaft axis. The plunger pumping system realizes static distribution of the liquid by the cylinder body, reduces energy loss and improves conveying pressure. The plurality of guide posts realize the inclination adjustment of the limiting surface during rotation through the driving of the actuating mechanism to the inclination plate, so that the movement strokes of the swash plate and the plunger are sequentially changed, and the adjustable and controllable pumping flow is realized.

Description

Integrated adjustable pump

Technical Field

The invention belongs to the technical field of pumps, and particularly relates to an integrated adjustable pump.

Background

In the field of hydraulic systems and fluid delivery, a plunger pump is a commonly used efficient pump, the core components of the plunger pump are a cylinder body and a plunger, and the basic working principle is that the plunger reciprocates in the cylinder body to cause volume change in the cylinder body so as to form pressure difference, thereby driving the flow of liquid and realizing the suction and discharge of the liquid. The plunger pump has the advantages of small volume, high pressure, high efficiency and the like because of compact structure, a plurality of plungers can be simultaneously arranged in one cylinder body, and the stroke is continuous. The plunger pump has various structural forms, including a swash plate type plunger pump and a inclined shaft type plunger pump.

The driving shaft of the inclined shaft plunger pump forms a certain inclined angle with the cylinder body, and when the driving shaft rotates, the cylinder body is driven to rotate together, so that the plunger in the cylinder body generates reciprocating motion. Such pumps are capable of withstanding relatively high operating pressures due to low friction and energy losses, but are limited by the form of the transmission, which typically does not allow for adjustment of the pumping flow. The swash plate type plunger pump is characterized in that a plurality of plungers are installed in a cylinder body, and reciprocating motion of the plungers is realized by a swash plate forming a certain angle with a driving shaft. When the driving shaft rotates, the cylinder body is driven to rotate, the cylinder body drives a plurality of plungers in the cylinder body to synchronously revolve, and under the transmission action of the plungers, the swash plate is always positioned on the same inclined plane to rotate under the limit of the inclination plate, so that the plungers generate reciprocating motion in the cylinder body.

The angle of the swash plate type plunger pump can be limited and adjusted through the inclination plate (the inclination plate is controlled by a hydraulic cylinder to change the inclination angle), so that the pumping flow can be adjusted, and the characteristic makes the swash plate type plunger pump particularly suitable for a system requiring variable flow. However, in order to realize the adjustable flow, the driving shaft needs to drive the whole cylinder body to rotate, and the oil distribution end of the cylinder body needs to realize the input and output of liquid through a static oil distribution disc, so that the friction loss between the cylinder body and the oil distribution disc, between the cylinder body and the casing and between the swash plate and the inclination disc is extremely large, and the load influence on the driving shaft caused by the rotation of the cylinder body is added, so that the working condition pressure range of the swash plate type plunger pump is smaller.

Disclosure of Invention

The present invention aims to provide an integrated adjustable pump to solve the above-mentioned problems of the prior art.

There is provided an integrated adjustable pump comprising:

the pump body comprises a shell and a cylinder body, and the cylinder body is fixedly connected with one end of the shell;

The oil distribution assembly comprises a sloping cam plate, a ball head support, a plurality of ball head connecting rods and a plurality of plungers, wherein the plungers are arranged in the cylinder body, one end of the ball head support is fixedly connected with the cylinder body, the other end of the ball head support is hinged with the sloping cam plate, and two ends of the ball head connecting rods are respectively hinged with the sloping cam plate and the corresponding plungers;

the driving assembly comprises a driving shaft, a limit disc, an inclination disc and a plurality of guide posts, wherein the driving shaft is rotationally connected with the machine shell and movably penetrates through the inclination disc and then is fixedly connected with the limit disc, the guide posts are circumferentially arranged on the inclination disc, one end of each guide post is in spherical hinge connection with the inclination disc, and the other end of each guide post movably penetrates through the limit disc and then is in contact with the swash plate;

And the actuating mechanism is used for driving the dip angle disc to rotate so as to change the dip angle relative to the axis of the driving shaft.

As a further embodiment of the present invention, one end of the guide post, which contacts the swash plate, forms an arc surface.

As a further embodiment of the invention, the end part of the guide post is connected with a ball head in a rolling way, and the guide post is contacted with the sloping cam plate through the ball head.

In a further embodiment of the invention, the actuating mechanism is an electromagnet, the actuating mechanism surrounds and is fixed on the casing relative to the periphery of the driving shaft in a circular ring shape, the dip angle disc is provided with a magnet disc in a circumferential ring, the magnet disc is arranged opposite to the actuating mechanism, and the dip angle disc is provided with an elastic resistance piece.

As a further embodiment of the invention, a bidirectional spherical hinge is arranged on the driving shaft at the contact part with the dip angle disc, and the inner wall of the dip angle disc is attached to the shape of the bidirectional spherical hinge.

As a further embodiment of the invention, the elastic resistance piece is a torsion spring, the torsion spring is arranged in the bidirectional spherical hinge, one end of the torsion spring is arranged in the bidirectional spherical hinge, and the other end of the torsion spring is arranged in the dip angle disc.

As a further embodiment of the invention, the periphery of the bidirectional ball joint is provided with a plurality of splines which are arranged along the radial direction of the driving shaft, and the splines are spherical surfaces which extend along the axial direction of the driving shaft and are outwards convex relative to the bidirectional ball joint.

As a further embodiment of the invention, the end spherical hinge of the guide post is elastically connected with the dip angle disc.

As a further embodiment of the invention, an oil cavity is formed between the inside of the shell and the cylinder body, a conveying channel is formed inside the cylinder body, a communicating channel is formed inside the plunger, the communicating channel communicates the oil cavity with the conveying channel, a first one-way valve is arranged in the communicating channel, and a second one-way valve is arranged in the conveying channel.

Compared with the prior art, the invention has the beneficial effects that:

1. The pumping system provided by the invention drives the swash plate to move through the driving component with the inclined rotating surface. Because the swash plate has the degree of freedom of relative rotation with the drive assembly, and the swash plate receives the spacing effect of bulb support and a plurality of plunger simultaneously for each constitutional unit on the swash plate realizes that it carries out reciprocating motion's motion form in the axial of drive shaft, and then makes the swash plate drive the plunger through the bulb connecting rod and carries out reciprocating motion in the cylinder body, and need not to make the cylinder body carry out synchronous rotation. The plunger pumping system realizes static distribution of the liquid by the cylinder body, reduces energy loss and improves conveying pressure.

2. The inclined rotating surface of the driving assembly is formed by a plurality of guide posts which are oppositely arranged front and back in the axial direction of the driving shaft, the guide posts can synchronously rotate along with the driving shaft through the limit of the limit disc, and then each structural unit on the driving swash plate is guided to realize front and back reciprocating motion through limit of the swash plate. Because the contact area between the guide post and the swash plate is extremely small, the friction belt of the swash plate is limited in an extremely small range, so that the wear rate of the swash plate is reduced.

3. The inclination angle of the inclination plate can be changed under the drive of the actuating mechanism, and the plurality of guide posts can slide relative to the limiting plate through the rotation of the inclination plate so as to change the relative position between each guide post and further change the inclined limiting surface formed by the end parts of the plurality of guide posts. After the inclination angle of the inclined limiting surface is changed, the limiting angle of the swash plate is changed simultaneously during rotation, so that the front-back reciprocating motion stroke of each structural unit on the swash plate is enlarged or reduced, the sliding stroke of the plunger is further changed, and the pumping flow control of the pumping system is realized.

Drawings

In order to more clearly illustrate the embodiments of the present drawings or the technical solutions in the prior art, the drawings that are required to be used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present drawings, and that other drawings may be obtained according to the structures shown in these drawings without inventive effort to a person skilled in the art.

FIG. 1 is a schematic diagram of the overall structure of an integrated adjustable pump;

FIG. 2 is a diagram showing an oil distribution structure of a cylinder and a plunger provided by the invention;

fig. 3 is a schematic view of a part of the structure of the guide post provided by the invention.

The device comprises a shell, a cylinder body, a conveying channel, a second one-way valve, a 13, an oil cavity, a 21, a sloping cam plate, a 22, a ball head support, a 23, a ball head connecting rod, a 24, a plunger, a 241, a communicating channel, a 242, a first one-way valve, a 31, a driving shaft, a 311, a two-way ball hinge, a 312, a torsion spring, a 313, a spline, a 32, a limiting disc, a 33, an inclination disc, a 34, a guide post, a 341, a ball head, a 35, a magnet disc and a 4, and an actuating mechanism.

Detailed Description

The present application will be described and illustrated with reference to the accompanying drawings and examples in order to make the objects, technical solutions and advantages of the present application more apparent. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the application. All other embodiments, which can be made by a person of ordinary skill in the art based on the embodiments provided by the present application without making any inventive effort, are intended to fall within the scope of the present application.

It is apparent that the drawings in the following description are only some examples or embodiments of the present application, and it is possible for those of ordinary skill in the art to apply the present application to other similar situations according to these drawings without inventive effort. Moreover, it should be appreciated that while such a development effort might be complex and lengthy, it would nevertheless be a routine undertaking of design, fabrication, or manufacture for those of ordinary skill having the benefit of this disclosure, and thus should not be construed as having the benefit of this disclosure.

However, unnecessary detailed description may be omitted. For example, detailed descriptions of well-known matters and repeated descriptions of the actual same structure may be omitted. This is to avoid that the following description becomes unnecessarily lengthy, facilitating the understanding of those skilled in the art. Furthermore, the drawings and the following description are provided for a full understanding of the present application by those skilled in the art, and are not intended to limit the subject matter recited in the claims.

Referring to fig. 1, an integrated adjustable pump according to an embodiment of the present invention includes a pump body, an oil distribution assembly, a driving assembly, and an actuator 4. The pump body includes casing 11 and cylinder body 12, and cylinder body 12 and the one end fixed connection of casing 11. The oil distribution assembly comprises a swash plate 21, a ball bearing 22, a plurality of ball connecting rods 23 and a plurality of plungers 24, wherein the plungers 24 are arranged in the cylinder body 12, one end of the ball bearing 22 is fixedly connected with the cylinder body 12, the other end of the ball bearing 22 is hinged with the swash plate 21, and two ends of the ball connecting rods 23 are respectively hinged with the swash plate 21 and the corresponding plungers 24. The driving assembly comprises a driving shaft 31, a limiting disc 32, an inclination disc 33 and a plurality of guide posts 34, wherein the driving shaft 31 is rotationally connected with the shell 11 and movably penetrates through the inclination disc 33 to be fixedly connected with the limiting disc 32, the guide posts 34 are circumferentially arranged along the inclination disc 33, one end of each guide post 34 is in spherical hinge connection with the inclination disc 33, and the other end of each guide post is movably penetrated through the limiting disc 32 to be in contact with the swash plate 21. The actuator 4 is used to drive the tilt disc 33 in rotation to change the tilt angle relative to the axis of the drive shaft 31.

The oil distribution assembly is integrally arranged inside the cylinder body 12 and the shell 11, and the driving assembly and the actuating mechanism 4 are integrally arranged inside the shell 11. The cylinder block 12 is fixed at one end of the housing 11, and the driving shaft 31 is introduced from the other end of the housing 11 and is rotatably connected to the housing 11. The driving flow of the adjustable pump of the present invention is specifically that the driving shaft 31 rotates and synchronously drives the limiting plate 32 fixedly connected with the driving shaft to rotate. The stopper plate 32 is provided with a plurality of guide posts 34 disposed forward and backward in the axial direction of the drive shaft 31 in the circumferential direction, and the ends of the plurality of guide posts 34 form stopper surfaces having a certain range of travel and exert a stopper driving action on the swash plate 21 during rotation. The center of the swash plate 21 is ball-hinged on the cylinder body 12 through the ball head support 22, the rotation freedom degree between the swash plate 21 and the cylinder body 12 is limited by the limit of the plunger 24 at the peripheral part of the swash plate 21, so that each section of the swash plate 21 can reciprocally rotate at a certain angle on a corresponding plane taking the ball hinge of the ball head support 22 as the center, and further the plunger 24 at a corresponding part is driven to reciprocally slide in the cylinder body 12 through the ball head connecting rod 23, thereby realizing volume change in the cylinder body 12.

The swash plate 21 and the plunger 24 are hinged through spherical hinges at two ends of the ball connecting rod 23, so that the size change between the section of the swash plate 21 and the plunger 24 when the section rotates on the ball support 22 can be adapted, and the interference problem is avoided.

When the displacement of the pump needs to be regulated, the actuator 4 drives the inclination disc 33 to rotate so as to change the inclination angle of the inclination disc 33, the guide posts 34 on each circumferential direction are respectively pulled back or pushed forward in the rotation process of the inclination disc 33, and the guide posts 34 are ensured to move along the axial direction of the driving shaft 31 under the limiting action of the limiting disc 32. Further, the inclination angle of the inclined guide surface formed by the end portions of the respective guide posts 34 is changed with the rotation of the inclination plate 33, so that the stroke expansion or contraction change is generated in association with the wave-shaped movement locus of the swash plate 21 when the swash plate 21 is rotationally slid, and the movement stroke of the plunger 24 is changed to realize the flow rate adjustment.

Wherein, the end spherical hinge of the guide post 34 is elastically connected with the dip angle disk 33. An elastic cushion is arranged between the spherical hinge and the hinge support of the tilt disc 33, and the elastic cushion can be a rubber cushion and the like, so that the guide post 34 and the tilt disc 33 have a tiny translational degree of freedom besides a rotational degree of freedom. When the tilt disc 33 rotates, an automatic adaptation is achieved by a small movement between the guide post 34 and the tilt disc 33, avoiding interference problems due to hard connection.

Specifically, one end of the guide post 34 in contact with the swash plate 21 forms an arc surface. The arc surface can make the guide post 34 smoothly transition when sliding relative to the swash plate 21, avoid the sharp part on the guide post 34 from generating sliding injury to the surface of the swash plate 21, and make the contact area of the guide post 34 and the swash plate 21 maintain at a small degree no matter what angle the guide post 34 contacts with, thereby reducing the friction belt area generated by the guide post 34 on the surface of the swash plate 21 to the greatest extent.

Further, as shown in fig. 1 and 3, the end of the guide post 34 is connected with a ball 341 in a rolling manner, and the ball 341 is partially wrapped inside the guide post 34 and has a rolling degree of freedom in all directions in the guide post 34, and is partially exposed to the outside to contact the swash plate 21. When the guide post 34 slides relative to the swash plate 21, the ball 341 interacts with the swash plate 21 in rolling contact, thereby greatly reducing friction and reducing wear between the guide post 34 and the swash plate 21. A plurality of balls with smaller volume can be filled between the ball head 341 and the inner wall of the guide column 34, so that the ball head 341 can slide smoothly in the guide column 34.

Specifically, the actuator 4 is an electromagnet, and the actuator 4 is annular and surrounds and is fixed to the housing 11 with respect to the periphery of the drive shaft 31. The dip angle disc 33 is circumferentially provided with a magnet disc 35, the magnet disc 35 is made of metal with magnetism, and the magnet disc 35 is arranged opposite to the actuator 4. When the actuator 4 is not energized, it has no magnetism, and does not act against the magnet plate 35, so that the tilt plate 33 is in a free state. When the actuator 4 is energized, a magnetic field is generated to attract or repel the magnet disc 35, so as to control the rotation of the tilt disc 33, and further control the sliding of the plurality of guide posts 34, and the rotation angle of the tilt disc 33 can be controlled by the intensity of the energizing current of the electromagnet. The elastic resistance member is used to apply a reverse force to the tilt disc 33 and to restrain the tilt disc 33 in an initial position when the actuator 4 applies a force to the tilt disc 33. The electromagnet can maintain the magnetic field intensity by maintaining the current intensity, so that the balance state between the actuating mechanism 4 and the dip angle disc 33 is maintained, and the dip angle disc 33 is ensured not to automatically change dip angle to influence the pumping displacement when rotating.

Further, a bi-directional spherical hinge 311 is provided on the driving shaft 31 at a portion contacting the tilt disk 33, and the inner wall of the tilt disk 33 is fitted to the shape of the bi-directional spherical hinge 311. The tilt disc 33 can stably rotate by taking the bidirectional spherical hinge 311 as a central shaft, and the degree of freedom of the tilt disc 33 in the axial direction of the driving shaft 31 can be blocked by forming a limit between the circular arc surface of the bidirectional spherical hinge 311 and the tilt disc 33, and only the degree of freedom of rotation is possessed, so that the relative distance between each guide post 34 and the swash plate 21 is ensured not to be changed due to the translation of the tilt disc 33.

The resilient resistance is embodied as a torsion spring 312. The torsion spring 312 is disposed in the bi-directional spherical hinge 311, one end of the torsion spring 312 is disposed in the bi-directional spherical hinge 311 and the other end is disposed in the tilt disk 33. The torsion spring 312 is located between the bidirectional ball pivot 311 and the tilt disc 33, and is used for giving an initial limiting point to the tilt disc 33 and giving a reverse acting force to the tilt disc 33 when an interaction force is generated between the actuator 4 and the magnet disc 35. Since the acting force exerted on the tilt disc 33 by the actuator 4 is fixed, and the larger the tilt angle of the tilt disc 33 is changed from the initial limit point, the larger the reverse acting force of the torsion spring 312 is, and when the tilt disc 33 rotates to a certain degree, a balance force is formed between the actuator 4 and the torsion spring 312 to maintain the state of the tilt disc 33 at this time. And when the actuator 4 is closed, the tilt disc 33 is reset by the torsion spring 312.

In one embodiment, the initial limit point created by torsion spring 312 acting on tilt disc 33 may be located in the most common displacement position of the regulated pump, where actuator 4 may not be activated or actuator 4 may be activated in a low power state. When the pump displacement is required to be regulated, repulsive force is generated between the actuating mechanism 4 and the magnet disc 35 to drive the tilt disc 33 to rotate in a direction of forming a vertical state trend with the driving shaft 31, and when the pump displacement is required to be regulated, attractive force is generated between the actuating mechanism 4 and the magnet disc 35 to drive the tilt disc 33 to rotate in a direction of forming a parallel state trend with the driving shaft 31. In this way, the power of the actuator 4 can be adjusted with a minimum adjustment range.

In this case, although the actuator 4 generates a magnetic field having the same strength and direction in the circumferential direction, when the respective structural points of the tilt disk 33 have different distances from the actuator 4 in the circumferential direction, the respective structural points of the tilt disk 33 differ from the actuator 4 in terms of the forces acting on the positions closer to the actuator 4, and the forces acting on the positions farther from the actuator are small. The entire circumferential direction of the tilt disc 33 is thus subject to repulsive or attractive forces, but due to the different distribution of forces, the tilt disc 33 is still driven in rotation. The initial posture of the tilt disk 33 by the restriction of the torsion spring 312 needs to be formed in an inclined shape with respect to the drive shaft 31. The magnet plate 35 may be provided only partially on the tilt plate 33, so that only a part of the structure of the tilt plate 33 acts on the actuator 4 to generate a magnetic field.

In another embodiment, the elastic resistance element is two springs, which are respectively located between the two oblique extremes of the tilt disc 33 and the limit disc 32. This solution also enables a limited effect on the tilting disk 33, but is not compact enough compared to the solution of the torsion spring 312, and is affected by centrifugal forces during rotation of the drive assembly, which is not suitable for using too long springs.

The bidirectional spherical hinge 311 is provided at the periphery thereof with a plurality of splines 313 arranged radially along the driving shaft 31, the splines 313 being spherical surfaces extending in the axial direction of the driving shaft 31 and having protrusions protruding outward with respect to the bidirectional spherical hinge 311. While maintaining the basic rotation function, the driving shaft 31 may transmit torque to the tilt disk 33 through the spline 313 to reduce the torsion force received when the guide post 34 drives the tilt disk 33 to rotate, which may enhance the overall stability of the driving assembly and reduce the number or size of the arrangement of the guide posts 34.

In one embodiment, referring to fig. 1 and 2, an oil chamber 13 is formed between the interior of the casing 11 and the cylinder 12, a delivery passage 121 is formed in the interior of the cylinder 12, a communication passage 241 is formed in the interior of the plunger 24, the communication passage 241 communicates the oil chamber 13 with the delivery passage 121, a first check valve 242 is provided in the communication passage 241, and a second check valve 122 is provided in the delivery passage 121.

When the plunger 24 moves toward the oil chamber 13, the volume of the oil distribution chamber space between the plunger 24 and the cylinder 12 increases to form negative pressure inside, the liquid in the oil chamber 13 pushes the first check valve 242 open through the communication channel 241 to enter the oil distribution chamber, and the second check valve 122 closes to prevent the liquid in the conveying channel 121 from entering the oil distribution chamber. When the plunger 24 moves toward the conveying passage 121, the volume of the oil distribution cavity between the plunger 24 and the cylinder 12 is reduced to form positive pressure inside, the first check valve 242 is closed to prevent liquid in the oil distribution cavity from entering the oil cavity 13, and the liquid in the oil distribution cavity pushes the second check valve 122 to enter the conveying passage 121 and be output outwards, so that a liquid discharge period is realized.

The first check valve 242 is composed of a spring and a valve ball, and the valve ball is abutted against one end of the communication channel 241 near the oil chamber 13 by the spring. The second check valve 122 is composed of a spring and a valve ball which is held against one end of the delivery passage 121 near the oil distributing chamber by the spring. The automatic control of the one-way valve can be realized.

It should be noted that the form of oil distribution between the plunger 24 and the cylinder 12 may be selected according to the need, or the oil chamber 13 may not be used to participate in oil distribution, but oil distribution passages may be provided between the cylinder 12 and the plunger 24. The present invention provides only one embodiment of an oil distribution mode and is not limited solely herein.

The present application is not limited to the above embodiment. The above embodiments are merely examples, and embodiments having substantially the same configuration and the same effects as those of the technical idea within the scope of the present application are included in the technical scope of the present application. Further, various modifications that can be made to the embodiments and other modes of combining some of the constituent elements in the embodiments, which are conceivable to those skilled in the art, are also included in the scope of the present application within the scope not departing from the gist of the present application.

Claims

1. An integrated adjustable pump, characterized by comprising:

A pump body, comprising a casing (11) and a cylinder body (12), wherein the cylinder body (12) is fixedly connected to one end of the casing (11);

An oil distribution assembly, comprising a swash plate (21), a ball head support (22), a plurality of ball head connecting rods (23) and a plurality of plungers (24), wherein the plurality of plungers (24) are arranged inside a cylinder body (12), one end of the ball head support (22) is fixedly connected to the cylinder body (12) and the other end is hinged to the swash plate (21), and the two ends of the plurality of ball head connecting rods (23) are respectively hinged to the swash plate (21) and the corresponding plungers (24);

A drive assembly, comprising a drive shaft (31), a limit plate (32), an inclining plate (33) and a plurality of guide columns (34); the drive shaft (31) is rotatably connected to the housing (11) and movably passes through the inclining plate (33) and then is fixedly connected to the limit plate (32); the plurality of guide columns (34) are arranged along the circumference of the inclining plate (33); one end of the guide column (34) is ball-jointedly connected to the inclining plate (33) and the other end of the guide column (34) movably passes through the limit plate (32) and then contacts the slanting plate (21);

An actuator (4) is used to drive the inclination plate (33) to rotate so as to change the inclination angle relative to the axis of the drive shaft (31).

2. An integrated adjustable pump according to claim 1, characterized in that the end of the guide column (34) in contact with the swash plate (21) forms an arc surface.

3. An integrated adjustable pump according to claim 2, characterized in that the end of the guide column (34) is rollingly connected with a ball head (341), and the guide column (34) is in contact with the swash plate (21) through the ball head (341).

4. An integrated adjustable pump according to claim 1, characterized in that the actuator (4) is an electromagnet, the actuator (4) is in a circular ring shape and surrounds the periphery of the drive shaft (31) and is fixed on the casing (11), the inclination plate (33) is provided with a magnet plate (35) along the circumferential ring, the magnet plate (35) is arranged opposite to the actuator (4), and an elastic resistance member is provided on the inclination plate (33).

5. An integrated adjustable pump according to claim 4, characterized in that a bidirectional ball joint (311) is provided at a portion of the drive shaft (31) that contacts the inclinometer plate (33), and an inner wall of the inclinometer plate (33) fits the shape of the bidirectional ball joint (311).

6. An integrated adjustable pump according to claim 5, characterized in that the elastic resistance member is a torsion spring (312), the torsion spring (312) is arranged in a two-way ball joint (311), one end of the torsion spring (312) is arranged in the two-way ball joint (311) and the other end is arranged in the inclination plate (33).

7. An integrated adjustable pump according to claim 5, characterized in that the bidirectional ball joint (311) is provided with a plurality of splines (313) arranged radially along the drive shaft (31) on the periphery thereof, and the splines (313) extend axially along the drive shaft (31) and have a spherical surface protruding outwardly relative to the bidirectional ball joint (311).

8. An integrated adjustable pump according to claim 1, characterized in that the end ball joint of the guide column (34) is elastically connected to the inclination plate (33).

9. An integrated adjustable pump according to claim 1, characterized in that an oil chamber (13) is formed between the inside of the casing (11) and the cylinder body (12), a delivery channel (121) is formed inside the cylinder body (12), a connecting channel (241) is formed inside the plunger (24), the connecting channel (241) connects the oil chamber (13) with the delivery channel (121), a first one-way valve (242) is provided in the connecting channel (241), and a second one-way valve (122) is provided in the delivery channel (121).