CN114687975A

CN114687975A - Variable compact type electro-hydraulic integrated machine

Info

Publication number: CN114687975A
Application number: CN202011634601.XA
Authority: CN
Inventors: 钟彪
Original assignee: Individual
Current assignee: Shanghai Qiangtian Drive Technology Co ltd
Priority date: 2020-12-31
Filing date: 2020-12-31
Publication date: 2022-07-01

Abstract

The invention discloses a variable compact type electro-hydraulic all-in-one machine which comprises a hydraulic assembly, a motor rotor assembly, a motor stator assembly, a rotary drum, a shell assembly and a variable mechanism, wherein the hydraulic assembly comprises a flow distribution sliding disc pair, a flow distribution pair and a plunger pair, the flow distribution pair comprises an end part of a cylinder body and a flow distribution disc, the rotary drum is respectively connected with the cylinder body and the motor rotor assembly to enable the rotary drum, the cylinder body and the motor rotor assembly to synchronously rotate, the flow distribution sliding disc pair comprises a swash plate and a sliding disc supported on the swash plate, the sliding disc is of an integral disc structure, a static pressure oil film support is formed between the sliding disc and the swash plate, and the variable mechanism can enable output flow to be adjustable and comprises a swash plate angle control type variable structure and/or a motor rotating speed control type variable structure. The electro-hydraulic integrated machine has the advantages of being compact in structure, low in noise, efficient, energy-saving, high in power density, various and convenient in variable, long in service life and the like.

Description

Variable compact type electro-hydraulic integrated machine

Technical Field

The invention belongs to the technical field of power transmission and control, and particularly relates to a variable compact electro-hydraulic integrated machine.

Background

The hydraulic system plays an important role in modern industrial technology, and particularly has absolute advantages in terms of high-pressure, high power and quick response. At present, the hydraulic power unit that uses the motor as the prime mover among traditional hydraulic system is mostly formed by connecting a plurality of dispersed independent parts, as shown in fig. 1, the hydraulic transmission unit includes independent parts such as hydraulic pump 1, motor 2, shaft coupling 3, wherein motor 2 provides mechanical energy, drives hydraulic pump 1 operation, converts hydraulic pump 1 mechanical energy into hydraulic energy, and the hydraulic energy of hydraulic pump 1 output provides hydraulic energy for actuating mechanism. The structure has the problems of complex structure, large occupied volume, low power density, low efficiency, large assembly error, large noise, difficult heat dissipation, potential external leakage path and the like, and is particularly shown in the following aspects:

(1) large volume and low power density. As shown in fig. 1, independent components such as the motor 1, the hydraulic pump 2, the coupling 3 and the like are axially arranged, the axial length is long, the occupied space is large, and the device is not suitable for occasions with limited space such as mobile machinery, aerospace, ships and the like. Although the power density of the hydraulic pump is large, the power density is low if an energy conversion member such as an electric motor is included.

(2) The efficiency is low. Independent parts such as a motor, a hydraulic pump, a coupler and the like are connected in multiple positions, so that the hydraulic power unit is complex in structure, more in energy conversion and power transmission links, and prone to generating mechanical friction loss, pipeline pressure loss, leakage loss and the like.

(3) Cavitation noise and vibration are prone to occur. The motor and the hydraulic pump in the distributed power unit are connected by a coupler, the coaxiality of the motor and the hydraulic pump cannot be absolutely guaranteed, and mechanical vibration and noise are easily generated in the working process; the complicated pipeline connection causes the increase of fluid resistance, and local negative pressure is easily generated to cause the separation of bubbles, thereby generating cavitation noise and vibration. The noise control of the traditional hydraulic power unit usually takes an independent motor and an independent hydraulic pump as research objects, the noise reduction space is not large, the difficulty of further noise reduction is very high, and the integral noise reduction effect is not very obvious.

(4) Heat dissipation is difficult. The energy dissipation exists in the operation process of the motor, the motor is finally dissipated in the external environment in the form of heat, and in order to reduce the temperature of the motor, a fan is generally arranged for dissipating the heat, so that the problems of large noise and motor energy consumption are caused.

(5) External leakage is easy to occur. The seals at the pipeline connecting parts and the hydraulic pump shaft extension part between the hydraulic pump and the oil tank lead the sealing device to be corroded and worn under the long-term working condition so as to generate external leakage, thus causing environmental pollution and inconvenient management and maintenance.

(6) The forming process of shell parts such as hydraulic pumps, motors and the like is complex. The hydraulic pump and the motor are independent elements, the shell structure is complex, and the hydraulic pump and the motor need to be cast respectively, so that the casting and processing cost is increased, and the carbon emission in the casting process is increased.

Modern hydraulic transmission technology gradually develops towards the direction of integration and digitization. Many applications require a smaller, lighter, and less noisy hydraulic power source to handle complex environmental conditions. Especially, with global warming and energy shortage aggravation, the requirements of people on energy conservation, consumption reduction, cleanness, environmental protection and low-carbon emission are continuously improved, and the structure of the traditional distributed hydraulic power unit is gradually difficult to adapt to the development of modern industrial technology. However, under the prior art, in the process of integrating the hydraulic pump and the motor, some technical bottlenecks, such as variable, flow distribution, heat dissipation and the like, cannot be considered, so that the problems are considered, and a certain distance is left from the high integration.

Disclosure of Invention

The invention aims to: aiming at the problems existing in the traditional hydraulic tradition at present, a novel electro-hydraulic all-in-one machine with compact structure, low noise, high efficiency, energy conservation, high power density, various and convenient variables and durability is provided, and the electro-hydraulic all-in-one machine aims at promoting the electro-hydraulic high fusion and realizing the integrated electric liquid drive development.

The technical scheme of the invention has the implementation mode that: the utility model provides a compact electricity liquid all-in-one of variable which characterized in that: the hydraulic assembly comprises a flow distribution sliding disc pair, a flow distribution pair and a plunger pair, the flow distribution pair comprises the end part of a cylinder body and a flow distribution disc, the rotating drum is respectively connected with the cylinder body and the motor rotor assembly, so that the rotating drum, the cylinder body and the motor rotor assembly synchronously rotate, the flow distribution sliding disc pair comprises a swash plate and a sliding disc supported on the swash plate, the sliding disc is of an integral disc-shaped structure, a static pressure oil film support is formed between the sliding disc and the swash plate, and the variable mechanism can adjust output flow and comprises a swash plate angle control type variable structure and/or a motor rotating speed control type variable structure.

The variable compact electro-hydraulic integrated machine is characterized in that an end seat is arranged in a shell cavity of the shell assembly, a valve plate is supported on the end seat, the valve plate is provided with a low-pressure flow distribution port communicated with a plunger hole of a cylinder body, a swash plate is supported on a rear end cover, the end seat is provided with an oil inlet hole and an oil inlet groove which is opened to the shell cavity, and the oil inlet hole is respectively communicated with the oil inlet groove of the end seat and the low-pressure flow distribution port of the valve plate.

The variable compact type electro-hydraulic integrated machine is characterized in that a low-pressure flow distribution window and a high-pressure flow distribution window are arranged on a swash plate, the low-pressure flow distribution window and the high-pressure flow distribution window are respectively communicated with an oil inlet and an oil outlet which are arranged on a rear end cover, the oil inlet on the rear end cover is provided with an oil path which leads to the low-pressure flow distribution window on the swash plate and an oil path which leads to a cavity of a shell through an oil inlet fork, when the variable compact type electro-hydraulic integrated machine works, low-pressure oil enters a plunger hole of a cylinder body from an oil inlet groove of an end seat through the low-pressure flow distribution port of the flow distribution plate and the low-pressure flow distribution window of the swash plate, and high-pressure oil is discharged from the high-pressure flow distribution window of the swash plate through a single path, so that the hydraulic oil is sucked and discharged.

The variable compact type electro-hydraulic integrated machine is characterized in that the variable mechanism is a swash plate angle control type variable structure and comprises a variable piston, a control valve and a variable spring, a cylindrical sliding arc surface formed in a cylindrical shape is arranged on a bearing surface, opposite to the rear end cover, of the swash plate, the variable piston drives the swash plate to slide on the cylindrical sliding arc surface, a groove-shaped low-pressure port and a groove-shaped high-pressure port formed in a groove shape are formed in the cylindrical sliding arc surface of the swash plate, and the groove-shaped low-pressure port and the groove-shaped high-pressure port are respectively communicated with an oil inlet and an oil outlet in the rear end cover correspondingly.

The variable compact type electro-hydraulic integrated machine is characterized in that a high-pressure flow distribution window is arranged on a swash plate, the high-pressure flow distribution window is communicated with an oil outlet arranged on a rear end cover, an oil inlet on the rear end cover is communicated with a shell cavity, low-pressure oil enters the shell cavity from the oil inlet on the rear end cover, when the variable compact type electro-hydraulic integrated machine works, the low-pressure oil in the shell cavity enters a plunger hole of a cylinder body through a low-pressure flow distribution port of the flow distribution plate in a one-way mode from an oil inlet groove of an end seat, and the high-pressure oil is discharged from the high-pressure flow distribution window of the swash plate in a one-way mode, so that the suction and the discharge of hydraulic oil are realized.

The variable compact type electro-hydraulic integrated machine is characterized in that the variable mechanism is a swash plate angle control type variable structure and comprises a variable piston, a control valve and a variable spring, a cylindrical sliding arc surface which is formed into a cylindrical shape is arranged on a bearing surface, opposite to the rear end cover, of the swash plate, the variable piston drives the swash plate to slide on the cylindrical sliding arc surface, a groove-shaped high-pressure port is formed in the cylindrical sliding arc surface of the swash plate, and the groove-shaped high-pressure port is correspondingly communicated with an oil outlet.

The variable compact type electro-hydraulic all-in-one machine is characterized in that the variable mechanism is set to be a motor rotating speed control type variable structure, the variable mechanism comprises a controller, the controller is a variable frequency type controller, the motor rotor assembly comprises a rotor iron core connected with the peripheral surface of the rotary drum and a rotor winding embedded in the rotor iron core, and the rotating speed of the motor rotor assembly is changed under the control action of the controller, so that the variable output flow is realized.

The variable compact electro-hydraulic all-in-one machine is characterized in that the variable mechanism is set to be a motor rotating speed control type variable structure and comprises a controller and an encoder, the controller is a servo controller, the motor rotor assembly comprises a rotor iron core connected with the outer peripheral surface of a rotary drum and a permanent magnet embedded in the rotor iron core, one end of a main shaft is connected with the encoder, and the motor rotor assembly can change rotating speed under the control action of the controller, so that variable output flow is achieved.

The variable mechanism of the variable compact electro-hydraulic all-in-one machine is a swash plate angle control type and motor rotating speed control type combined variable structure, the variable mechanism comprises a controller, the controller comprises a variable frequency type or servo type controller, and the combined variable structure can reasonably match working conditions and load changes of the motor according to actual conditions.

The variable compact type electro-hydraulic integrated machine is characterized in that impellers are arranged in the end seat and on the main shaft, a plurality of communicating holes and oil inlet holes communicated with low-pressure flow distribution ports of the flow distribution plate are formed in the end seat, and the impellers are driven by the main shaft to accelerate low-pressure oil in the cavity of the shell to enter the plunger holes through the communicating holes and take away heat through the oil inlet holes.

The variable compact type electro-hydraulic all-in-one machine is characterized in that the hydraulic assembly is of a shaft support type structure, the variable compact type electro-hydraulic all-in-one machine further comprises a first bearing and a second bearing, the axis of a main shaft of the main shaft is overlapped with the axis of a cylinder body, one end of the main shaft penetrates through an end seat to a front end cover and is supported on the first bearing, the other end of the main shaft penetrates through a rear end cover and is supported on the second bearing, the cylinder body is supported on the main shaft and is connected with the main shaft through a key to realize synchronous rotation, the plunger pair comprises a plunger hole wall of the cylinder body and a plunger, and the plunger reciprocates in a plunger cavity of the cylinder body to realize oil suction and discharge work.

The variable compact electro-hydraulic all-in-one machine comprises a hydraulic assembly, a fourth bearing and a fifth bearing, wherein the hydraulic assembly is of a rotary drum supporting structure, the fourth bearing and the fifth bearing are respectively clamped between a rotary drum and a shell assembly, a motor rotor assembly and the hydraulic assembly are supported on the shell assembly through the rotary drum, the fourth bearing and the fifth bearing and realize synchronous rotation, a plunger pair comprises a plunger hole wall of a cylinder body and a plunger, and the plunger reciprocates in a plunger cavity of the cylinder body to realize oil suction and discharge work.

Based on the technical scheme, the invention has the beneficial effects that:

(1) the invention has small volume and high power density. The traditional hydraulic power unit has the advantages that independent parts such as a motor, a hydraulic pump and a coupling are axially arranged, the axial length is long, the occupied space is large, the axial length of the electro-hydraulic integrated machine is reduced by more than 60%, the occupied space is reduced by more than 50%, the motor and the hydraulic pump are highly integrated, the integral power density is large, and the electro-hydraulic integrated machine is particularly suitable for occasions with limited space and large required power density such as engineering machinery, electric automobiles, robots, aerospace and ships.

(2) The invention solves the problems of variable, flow distribution and heat dissipation. The traditional electro-hydraulic integrated machine cannot give consideration to the problems of variable, flow distribution, heat dissipation and the like, so that the problems are considered. The structure of the flow distribution sliding disc pair adopted in the invention integrates the functions of flow distribution, variable inclination, static pressure support and self-cooling in the flow distribution sliding disc pair, the sliding disc and the swash plate adopt the existing optimal end surface oil film supporting mode and have the flow distribution function, and meanwhile, the flow distribution sliding disc pair can be realized by changing the inclination mode of the swash plate or the modes of motor speed change and the like, so that the variable diversification and convenience are realized, and the double-end surface oil inlet mode can also enable the heat dissipated in the cavity of the shell to enter a hydraulic system to realize self-cooling.

(3) The invention has high efficiency. The motor and the hydraulic pump are highly integrated, so that connecting parts such as a coupler and an air cooling device are omitted, energy conversion and power transmission links and extra energy loss of the air cooling device are reduced, and mechanical friction loss, pipeline pressure loss, leakage loss and the like are greatly reduced.

(4) The invention reduces noise and vibration obviously. The main sources of noise and vibration in conventional distributed power units are: mechanical vibration and noise generated by coaxiality errors of the connection of the motor, the hydraulic pump and the coupling, cavitation noise and vibration generated by the increase of fluid resistance caused by the connection of complex pipelines, and noise and vibration generated by an air cooling device of the motor; the electro-hydraulic integrated machine is highly integrated, the motor and the hydraulic pump are coaxial and share the shell, a coupler, an air cooling device and a connecting pipeline are eliminated, the influence of the three on noise and vibration is fundamentally eliminated, and the noise is obviously reduced.

(5) The invention has self-cooling and easy heat dissipation. Energy dissipation exists in the operation process of a traditional motor, and finally the energy is dissipated in an external environment in a heat mode, an air cooling device or a water cooling device needs to be additionally arranged.

(6) The invention has long service life and high reliability. The electro-hydraulic integrated machine is highly integrated, and all mechanical parts are highly integrated, so that the structural complexity is simplified; the sliding disc in the flow distribution sliding disc pair is of an integral structure, the plunger in the plunger pair is of a conical structure, the unique design of the two sliding disc pairs obviously reduces the lateral force of the plunger acting on the cylinder body, obviously improves the working conditions of the three friction pairs, improves the oil film stability of the friction pairs, and enables the hydraulic rotor part to have higher speed, higher pressure, higher flow and longer service life; the self-cooling double-end-face oil inlet structure design can enable key parts such as a motor stator, a rotor and a hydraulic three-large friction pair to be always immersed in lubricating low-temperature oil liquid, prevent the motor stator and the rotor from being burnt out and prevent oil films of the three-large friction pair from being stable, and enables the oil inlet amount on the oil inlet side to be remarkably increased, so that the self-priming capacity and the self-priming rotating speed can be greatly improved, and the damage of cavitation to the three-large friction pair is reduced.

(7) The invention reduces external leakage. The electro-hydraulic integrated machine is highly integrated, so that the sealing device is prevented from being corroded and abraded to generate external leakage under the long-term working condition by sealing at a plurality of pipeline connecting parts and a hydraulic pump shaft extension part, and environmental pollution and inconvenience in management and maintenance are caused.

(8) The invention is highly compatible with the future industrial technology development trend. The electro-hydraulic integrated machine is highly integrated, meets the development requirements of future industrial technologies, and develops towards environmental protection, energy conservation, integration, digitization and intellectualization.

Drawings

Fig. 1 is a schematic structural diagram of a conventional hydraulic power unit.

FIG. 2 is a schematic structural diagram of the electro-hydraulic integrated machine.

Fig. 3 is an embodiment of the electrohydraulic all-in-one machine in the invention.

FIG. 4 is a cross-sectional view taken along line A-A of FIG. 3 according to the present invention.

FIG. 5 is an internal liquid flow diagram of the electro-hydraulic integrated machine in the invention.

FIG. 6 is a plan view of one end of the slide plate of the present invention.

Fig. 7 is a sectional view taken along line B-B of the structure of the slide plate of fig. 6 according to the present invention.

Fig. 8 is a plan view of the other end of the slide plate in the present invention.

FIG. 9 is a plan view of the bearing surface of one end of the swash plate of the present invention.

FIG. 10 is a plan view of the bearing surface of the other end of the swash plate in the present invention.

FIG. 11 is a plan view of a bearing surface at one end of the port plate of the present invention.

Fig. 12 is a plan view of one end of the cylinder body in the present invention.

FIG. 13 is a cross-sectional view of the drum of the present invention taken along the axis thereof.

FIG. 14 is a plan view of one side of the drum of the present invention.

FIG. 15 is a cross-sectional view of the end block of the present invention taken along the axis.

FIG. 16 is a cross-sectional view taken along line C-C of FIG. 15 of the present invention.

FIG. 17 is another embodiment of the electrohydraulic all-in-one machine of the present invention.

FIG. 18 shows a drum-supported electro-hydraulic hybrid embodiment of the present invention.

FIG. 19 is a cross-sectional view taken along line A-A of FIG. 18 according to the present invention.

FIG. 20 shows an embodiment of a servo-controlled electro-hydraulic integrated machine according to the present invention.

FIG. 21 shows an embodiment of the combined variable electro-hydraulic all-in-one machine of swash plate inclination angle control and servo control in the invention.

The labels in the figure are: 1 is a hydraulic pump, 2 is a motor, 3 is a coupler, 4 is an air cooling device, 5 is an electro-hydraulic integrated machine, 6 is an outlet box, 7 is a lifting ring, 8 is a motor stator component, 8a is a stator core, 8b is a stator winding, 9 is a motor rotor component, 9a is a rotor core, 9b is a rotor winding, 9C is a permanent magnet, 9d is an end ring, 10 is a main shaft, 10C is a main shaft axis, 11 is a rotary drum, 12 is a connecting part, 13 is an oil through hole, 14 is a connecting key, 15 is a bulge, 16 is a first stop block, 17 is a second stop block, 21 is a first bearing, 22 is a second bearing, 23 is a third bearing, 24 is a fourth bearing, 25 is a fifth bearing, 31 is a shell, 32 is a front end cover, 33 is a rear end cover, 33a is an oil inlet, 33b is an oil outlet, 33C is an oil inlet fork, 34 is a shell cavity, 35 end seats, 36 is an end seat communicating hole, 37 is an oil inlet groove, 38 is an oil inlet, 39 is a supporting spacer, 40 is a swash plate, 41 is a swash plate supporting surface, 41a is a supporting stop, 42 is a flow distribution oil groove, 43 is a low-pressure flow distribution window, 44 is a high-pressure flow distribution window, 45 is a cylindrical sliding arc surface, 46 is a groove-shaped low-pressure port, 47 is a groove-shaped high-pressure port, 50 is a sliding plate, 50C is a sliding plate axis, 51 is a sliding plate static pressure supporting surface, 52 is a sliding plate convex table surface, 53 is a sliding plate kidney-shaped hole, 54 is a sliding plate outer sealing portion, 55 is a sliding plate inner sealing portion, 56 is a sliding plate spacer sealing portion, 58 is a plunger ball socket, 60 is a pressure plate, 70 is a plunger, 71 is a plunger ball head, 72 is a plunger center hole, 73 is a tapered rod portion, 74 is a plunger portion, 80 is a cylinder body, 81 is a plunger hole, 82 is a main shaft assembling hole, 83 is a cylinder body static pressure supporting surface, 83a cylinder body convex table surface, 84 is a through oil hole, 85 is a cylinder body, 90 is a flow distribution plate, 91 is a supporting surface, 92 is a low-pressure flow distributing port, 100 is a central spring, 101 is a retainer ring, 102 is a spherical hinge, 110 is a swash plate angle control type variable structure, 111 is a variable piston, 112 is a control valve, 113 is a variable spring, 141 is a snap spring, 150 is an impeller, 160 is an encoder, 161 is a protective cover, 162 is an encoder joint, and 163 is a controller.

Detailed Description

The present invention will be described in detail below with reference to the accompanying drawings.

While this invention is susceptible of embodiment in many different forms, this specification and the accompanying drawings disclose only some specific forms as examples of the invention. The invention is not intended to be limited to the embodiments so described. The scope of the invention is given by the appended claims.

For convenience of description, the embodiment of the present invention is shown in a typical orientation such that when the central axis of the main shaft of the electrohydraulic all-in-one machine 5 is horizontally stationary, the front end cap 32 side is left, the rear end cap 33 is right, and the terms "longitudinal," "lateral," "up," "down," "front," "back," "left," "right," "horizontal," "bottom," "inner," "outer," and the like are used in the description with reference to this position, but for convenience of description and simplicity of description, and not to indicate or imply that the device or component being referred to must have a particular orientation, and that the device or component being referred to must be constructed and operated in a particular orientation, it is to be understood that the present invention can be manufactured, stored, transported, used, and sold in an orientation different from the position being described.

Example 1:

as shown in fig. 2 to 16, which are preferred embodiments of the electro-hydraulic integrated machine 5 of the present invention, in the illustrated preferred embodiments, the electro-hydraulic integrated machine 5 is a shaft support type structure, the electro-hydraulic integrated machine 5 includes a hydraulic assembly, a motor rotor assembly 9, a motor stator assembly 8, a drum 11, a housing assembly, a main shaft 10, a variable mechanism, a first bearing 21 and a second bearing 22, the hydraulic assembly includes a plunger pair, a flow distribution sliding plate pair and a flow distribution pair; the plunger pair comprises a plunger 70 and a plunger hole wall of a cylinder body 80, and preferably, the plunger 70 is of a conical structure with a central large hole in the center; the flow distribution sliding disc pair comprises a swash plate 40 and a sliding disc 50 supported on the swash plate 40, the sliding disc 50 is of an integral structure, and a static pressure oil film support is formed between the sliding disc 50 and the swash plate 40; the flow distribution pair comprises an end part of the cylinder body 80 and a flow distribution plate 90, the cylinder body 80 is abutted against the flow distribution plate 90, and a static pressure oil film support is formed between the cylinder body 80 and the flow distribution plate 90; a main shaft axis 10C of the main shaft 10 coincides with a cylinder axis of the cylinder 80, one end of the main shaft 10 penetrates through the end seat 35 to the front end cover 32 and is supported on the first bearing 21, the other end penetrates through the rear end cover 33 and is supported on the second bearing 22, and the cylinder 80 is supported on the main shaft 10 and is connected with the main shaft 10 through a key; the rotating cylinder 11 is respectively connected with the cylinder body 80 and the motor rotor assembly 9, so that the rotating cylinder 11, the cylinder body 80 and the motor rotor assembly 9 rotate synchronously, and the plunger 70 reciprocates in a plunger cavity of the cylinder body 80, thereby realizing oil suction and discharge work.

The motor includes but is not limited to an induction asynchronous motor, a permanent magnet direct current motor, a permanent magnet synchronous motor, and the like, and preferably, the motor is an induction motor or a permanent magnet synchronous motor.

Specifically, the motor stator assembly 8 includes a stator core 8a, a stator winding 8b, and the like, where the stator core 8a is a component of a motor magnetic circuit and is formed by punching and laminating a thin silicon steel sheet coated with insulating paint on a surface thereof, the outer circumferential surface of the stator core is fixedly connected with the housing 31, the inner circumferential surface of the stator core 8a is provided with a plurality of notches (not shown), the stator winding 8b is embedded in the notches of the stator core 8a to generate a rotating magnetic field, the stator winding 8b is wound by an insulated copper wire or an insulated aluminum wire, and an outlet end of the stator winding 8b leads to the outlet box 6 disposed on the housing 31.

Specifically, the motor rotor assembly 9 includes a rotor core 9a, a rotor winding 9b, and the like. The rotor core 9a is also a component of a magnetic circuit of a motor, and is also formed by punching and laminating a thin silicon steel sheet coated with insulating paint on the surface, the inner circumferential surface of the rotor core 9a is fixedly connected with the rotating drum 11, the side surfaces of both sides of the rotor core 9a abut against the protruding portion 15 of the rotating drum 11 through the first stopper 16 to limit the axial displacement of the rotor core 9a and the rotating drum 11, the outer circumferential surface of the rotor core 9a is provided with a plurality of notches (not shown), the rotor winding 9b is embedded in the notches of the rotor core 9a to generate induced current, the rotor winding 9b includes, but is not limited to, a squirrel-cage structure and a winding structure rotor winding, wherein the squirrel-cage structure is formed by inserting copper bars or aluminum bars into the slots on the rotor core 9a as guide bars and connecting the copper rings or the aluminum rings at both ends to form a cage-shaped structure.

A certain air gap is kept between the motor stator assembly 8 and the motor rotor assembly 9, so that reasonable power factor and starting performance are ensured when the motor runs. Alternatively, the air gap may be filled with cold oil at low pressure within the housing cavity 34 to dissipate heat from the motor stator assembly 8 and the motor rotor assembly 9.

Specifically, the variable mechanism is a swash plate angle control type variable structure 110, the swash plate angle control type variable structure includes variable pistons 111, a control valve 112 and a variable spring 113, the control valve 112 is connected with the rear end cover 33, a plurality of fluid passages are arranged in the control valve 112, the control valve 112 controls the movement of the variable pistons 111 by controlling oil entering the variable pistons, so as to change the angle of the swash plate, the control valve 112 can be set to a plurality of variable control modes including but not limited to constant pressure, constant flow, constant power and the like, and the variable spring 113 plays a role in resetting.

Specifically, a bearing surface of the swash plate 40 opposite to the rear end cover 33 is provided with a cylindrical sliding arc surface 45 which is shaped like a cylinder, the variable piston 111 drives the swash plate 40 to slide on the cylindrical sliding arc surface 45, the cylindrical sliding arc surface 45 of the swash plate 40 is provided with a groove-shaped low pressure port 46 and a groove-shaped high pressure port 47 which are shaped like a groove, and the groove-shaped low pressure port 46 and the groove-shaped high pressure port 47 are respectively communicated with the oil inlet 33a and the oil outlet 33b on the rear end cover 33.

Specifically, the flow distribution sliding disc pair comprises a sliding disc 50 and a swash plate 40 supported on a rear end cover 33, a static pressure bearing surface 51 of the sliding disc 50 is supported on the swash plate 40 and is tightly matched with the bearing surface of the swash plate 40, a plurality of sliding disc waist-shaped holes 53 are formed in one end of the sliding disc 50, a plurality of plunger ball sockets 58 are formed in the other end surface of the sliding disc 50, the sliding disc waist-shaped holes 53 in the sliding disc 50 penetrate through the plunger ball sockets 58, and a flow distribution oil groove 42 communicated with an oil inlet 33a and an oil outlet 33b in the rear end cover 33 is formed in the swash plate 40.

Specifically, the plunger pair comprises a plunger 70 and a cylinder hole wall, the plunger 70 is of a conical structure, and the plunger is provided with a large-hole plunger center hole 72 which is used for oil inlet and outlet and is communicated with a plunger ball socket 58 and a plunger hole 81.

Specifically, the flow distribution pair includes an end portion of the cylinder 80 and a flow distribution plate 90 supported on the end seat 35, an end surface of the end portion of the cylinder 80, which is opposite to the flow distribution plate 90, is provided with a cylinder static pressure bearing surface 83, the cylinder static pressure bearing surface 83 is supported on the flow distribution plate 90 and keeps a sliding fit with a bearing surface 91 of the flow distribution plate 90, and the flow distribution plate 90 is provided with a low-pressure flow distribution port 92, as shown in fig. 11.

Specifically, the outer peripheral surface of the rotary drum 11 is connected with the motor rotor assembly 9, a connecting part 12 extending inwards is arranged at the inner side of the rotary drum 11, a plurality of oil passing holes 13 are annularly arranged at the connecting part 12, the oil passing holes 13 are communicated with the shell cavities 34 at two sides so that low-pressure oil can smoothly pass through, and a connecting key 14 matched with the outer periphery of the cylinder 80 is arranged at the inner periphery of the connecting part 12; alternatively, the drum connecting portion and the cylinder body may include, but are not limited to, an interference fit connection, a bolt connection, and the like.

Furthermore, the rotating drum 11 is provided with a restraining device for restraining the axial movement, and the restraining device comprises convex parts 15 which are arranged on two sides of the rotating drum 11 and protrude outwards and used for restraining the axial displacement of the motor rotor, and a first stop 16 which is clamped between the motor rotor and the convex parts 15; the restraining device further comprises a second stopper 17 arranged on the outer circumferential direction of the cylinder 80 and used for restraining the axial displacement of the rotary drum 11, and the second stopper 17 is connected with the connecting part 12 of the rotary drum 11.

As shown in fig. 3 and 4, the housing assembly of the all-in-one electro-hydraulic machine 5 includes a housing 31, and a front end cover 32 and a rear end cover 33 connected to the housing 31, the front end cover 32 and the rear end cover 33 enclose a housing cavity 34 for accommodating the motor rotor assembly 9, the motor stator assembly 8 and the hydraulic assembly, the rear end cover 33 is used for closing one end opening of the housing 31, the front end cover 32 is used for closing the other end opening of the housing 31, an oil inlet 33a and an oil outlet 33b are provided on the rear end cover 33, an oil inlet fork 33c communicating the oil inlet 33a and the housing cavity 34 is further provided on the rear end cover 33, that is, when oil is absorbed, oil in the oil inlet 33a is divided into two parts, one part of the oil flows into the plunger hole 81 from the low-pressure distribution port 43 of the swash plate 40, and the other part of the oil flows into the housing cavity 34 through the oil inlet fork 33c, then enters the plunger hole 81 through the communication hole 36 of the end seat 35 and the low-pressure flow distribution hole 92 of the flow distribution plate 90, and when the cold oil of the part flows through the housing cavity 34, each friction pair, the motor rotor and the stator assembly part, which are arranged in the housing cavity 34, are immersed in the low-temperature oil, and heat generated by the motor stator assembly, the rotor assembly and the hydraulic friction pair is taken away and enters a hydraulic system, specifically, see a liquid flow diagram in the electro-hydraulic integrated machine in fig. 5. It should be noted that the front end cap 32 and the rear end cap 33 do not indicate or imply that the devices or elements referred to must be in a front-to-rear relationship, but merely for ease of description and simplicity of description, both are end caps that close the housing.

As shown in fig. 9, the flow distribution sliding disc pair is a bidirectional high-low pressure flow distribution sliding disc pair, the flow distribution sliding disc pair includes a sliding disc 50 and a swash plate 40 supported on the rear end cover 33, the swash plate 40 is provided with a low pressure flow distribution window 43 and a high pressure flow distribution window 44 which are separated from each other, and the low pressure flow distribution window 43 and the high pressure flow distribution window 44 are respectively communicated with the oil inlet 33a and the oil outlet 33b of the rear end cover 33; the flow distribution pair is a one-way low-pressure flow distribution pair, the flow distribution pair comprises a flow distribution disc 90 and a cylinder body 80 supported on the flow distribution disc 90, the flow distribution disc 90 and the cylinder body 80 form a static pressure oil film support in clearance fit, the static pressure oil film support and the cylinder body 80 are in sliding fit, one side of the flow distribution disc 90 opposite to the low-pressure side plunger plug hole 81 is provided with a low-pressure flow distribution port 92, and the low-pressure side plunger plug hole refers to a corresponding plunger hole into which low-pressure oil enters.

As shown in fig. 14 and 15, the end seat 35 is disposed between the flow distribution pair and the front end cover 32, the end seat 35 is connected with the front end cover 33 through bolts, the flow distribution plate 90 is supported on the end seat 35, the end seat 35 is provided with a communication hole 36, an oil inlet groove 37, an oil inlet hole 38 and a support spacer 39, the oil inlet groove 37 has a groove structure opening to the housing cavity 34, the support spacer 39 is used for supporting the groove walls on both sides of the oil inlet groove 37, and the oil inlet hole 38 is respectively communicated with the oil inlet groove 37 of the end seat 35 and the low-pressure flow distribution port 92 of the flow distribution plate 90. In particular, the end seat 35 may also be an extension of the front end cap 32, i.e. the end seat 35 and the front end cap 32 are of a unitary structure.

As shown in fig. 5, which is an internal fluid flow diagram of the electro-hydraulic integrated machine, the oil inlet 33a of the rear end cover 33 is provided with an oil path leading to the low-pressure flow distribution window 43 on the swash plate 40 and an oil path leading to the housing cavity 34 through the oil inlet fork 33c, when the electro-hydraulic integrated machine works, low-pressure oil enters the cylinder plunger hole 81 of the cylinder 80 from the oil inlet tank 37 of the end seat 35 through the low-pressure flow distribution port 92 of the flow distribution plate 90 and the low-pressure flow distribution window 43 of the swash plate 40, and high-pressure oil is discharged from the high-pressure flow distribution window 44 of the swash plate 40 in a single way, so that the suction and discharge of hydraulic oil are realized.

From the above analysis, it can be known that the structure has the characteristics of self-cooling and easy heat dissipation, which are specifically shown in the following steps: on one hand, key parts such as a motor stator, a rotor and a hydraulic three-large friction pair are always immersed in lubricating low-temperature oil, so that the motor stator and the rotor are prevented from being burnt out, oil films of the three-large friction pair are prevented from being stable, on the other hand, the oil inlet amount of the oil inlet side is obviously increased, the self-priming capacity and the self-priming rotating speed can be greatly improved, and the damage of cavitation to the three-large friction pair is reduced.

Meanwhile, the structure has the characteristics of small volume, high power density, high efficiency, low noise and the like. As shown in fig. 1, the hydraulic power unit is a conventional hydraulic power unit, independent components such as a motor 1, a hydraulic pump 2 and a coupling 3 are axially arranged, the axial length is long, and the occupied space is large, fig. 2 is an electro-hydraulic integrated machine of the invention, the axial length is reduced by more than 60%, the occupied space is reduced by more than 50%, the motor and the hydraulic pump are highly integrated into a whole, and the integral power density is large, so that the hydraulic power unit is particularly suitable for occasions with limited space and large required power density, such as engineering machinery, electric automobiles, robots, aerospace, ships and the like; the motor and the hydraulic pump are highly integrated, so that connecting parts such as a coupler and an air cooling device are omitted, energy conversion and power transmission links and extra energy loss of the air cooling device are reduced, and mechanical friction loss, pipeline pressure loss, leakage loss and the like are greatly reduced; the motor and the hydraulic pump are coaxial and share the shell, a coupler, an air cooling device and a connecting pipeline are omitted, the influence of the three on noise and vibration is fundamentally eliminated, and the noise is obviously reduced.

More specifically, a plurality of plunger ball sockets 58 are provided at positions opposing the plungers 70 in the circumferential direction of the end surface of the slide plate 50 on the side facing the cylinder 80, and as shown in fig. 6, 7 and 8, the plunger ball sockets 58 form recesses having substantially hemispherical openings in the end surface of the slide plate 50, the plunger ball sockets 58 support the plunger balls 71 in a state of being uniformly distributed at intervals along the circumference common to the slide plate axes 50C, and after the plungers 70 are attached to the plunger ball sockets 58, they are fixed to the end surface of the slide plate 50 by a pressing plate 60, so that the movement of the plungers 70 away from the end surface of the slide plate 50 is restricted. In particular, the means for fastening the plunger 70 to the front face of the slide plate 50 are also not limited to the use of a pressure plate, but, for example, a form-locking holding device (not shown) can also be provided on the slide plate 50, which can fasten the plunger ball 71 by a covering of more than 180 degrees.

As shown in fig. 7, a swash plate static pressure bearing surface 51 is provided on an end surface of the swash plate 50 facing the swash plate 40, the swash plate axis 50C forms a certain angle with the main shaft axis 10C, the swash plate static pressure bearing surface 51 is supported on the swash plate 40 and always slidably engages with the swash plate 40, a plurality of swash plate kidney holes 53 having a kidney shape are provided on the swash plate static pressure bearing surface 51, and preferably, the swash plate kidney holes 53 are uniformly distributed on the swash plate static pressure bearing surface 51 centering on the swash plate axis 50C, and the swash plate kidney holes 53 are communicated to the plunger ball socket 58.

Further, a projected slide plate land 52 extending toward the swash plate 40 side along the slide plate axis 50C is provided on the end surface of the slide plate 50 facing the swash plate 40, the slide plate land 52 is constituted by a region surrounded by an inner diameter R1 and an outer diameter R2, the slide plate land 52 and the swash plate 40 support surface are slidably abutted against each other, a plurality of slide plate waist holes 53 are provided on the slide plate land 52 at positions corresponding to the plunger ball sockets 58, and the slide plate waist holes 53 are preferably distributed on the slide plate land 52 at regular intervals on a common circumference centering on the slide plate axis 50C.

The sliding plate convex table surface 52 and the bearing surface of the swash plate 40 form effective static pressure oil film support, a sealing part used for sealing oil is arranged on the sliding plate convex table surface 52, the sealing part is arranged on the inner periphery and the outer periphery of the sliding plate kidney-shaped hole 53 in a state of surrounding the sliding plate kidney-shaped hole 53, the sealing part comprises a sliding plate inner sealing part 55, a sliding plate outer sealing part 54 and a sliding plate interval sealing part 56, the sliding plate inner sealing part 55 is distributed on the radial inner side and the radial outer side of the sliding plate kidney-shaped hole 53, the sliding plate inner sealing part 55 is a region formed by surrounding the inner edge of the sliding plate kidney-shaped hole 53 and the inner diameter R1 of the sliding plate convex table surface 52, the sliding plate outer sealing part 54 is a region formed by surrounding the outer edge of the sliding plate kidney-shaped hole 53 and the outer diameter R2 of the sliding plate convex table surface 52, the sliding plate interval sealing part 56 is a region of the interval convex table surface between the adjacent sliding plate kidney-shaped holes 53, and a certain reasonable clearance is always kept between the sealing part of the sliding plate convex table surface 52 and the bearing surface of the swash plate 40 to ensure that the oil film support is kept, so that the sliding plate convex table surface is kept The oil film leakage is at a reasonable level.

As shown in fig. 11, the cylinder block 80 has a cylindrical configuration with a circular cross section in the radial direction and is accommodated in the housing cavity 34 of the housing assembly, the cylinder block 80 has a plurality of plunger holes 81 uniformly distributed in the circumferential direction of the cylinder block axis and a spindle fitting hole 82 for accommodating the spindle 10 at the center, the cylinder block 80 has a plurality of plunger holes 81, and preferably, the number of plunger holes is generally set to 7 or 9; the main shaft 10 passes through a main shaft fitting hole 82 of the cylinder block 80 and is connected to the cylinder block 80 with a connection key provided on the outer circumferential surface of the shaft body, and the cylinder block 80 is supported on the main shaft 10 so as to move synchronously with the main shaft 10.

As shown in fig. 3 and 4, a cylinder static pressure bearing surface 83 is provided on an end surface of the cylinder 80 opposite to the port plate 90, the cylinder static pressure bearing surface 83 is supported on the port plate 90 and always keeps sliding fit with the port plate 90, a plurality of cylinder waist-shaped holes 85 in a waist shape are provided on the cylinder static pressure bearing surface 83, preferably, the cylinder waist-shaped holes 85 are uniformly distributed on the cylinder static pressure bearing surface 83 around the cylinder axis, and oil holes 84 for communicating the plunger hole 81 and the cylinder waist-shaped holes 85 are provided on the cylinder end.

In operation, hydraulic pressure acts on the cylinder end and is further transmitted to the port plate 90. in general, the axial force of the hydraulic pressure acting on the cylinder end is greater than the bearing force of the port plate 90 acting on the cylinder end through an oil film, so that the cylinder end slides against the port plate 90 through a layer of oil film all the time.

Specifically, the plunger 70 includes a plunger ball 71 having one end supported by the plunger ball socket 58 of the slide plate 50 and fixed to the end face of the slide plate via a pressing plate 60, a plunger center hole 72 for communicating a plunger hole 81 with the plunger ball socket 58, a tapered rod portion 73 having a conical outer peripheral surface, and a plunger portion 74 that is clearance-fitted to the cylinder plunger hole wall and is reciprocatable therein, the plunger ball 71 being spherical and slidably supported by the plunger ball socket 58 of the slide plate 50; the central hole 72 of the plunger is a large-aperture through hole structure and is used as an oil suction and/or discharge channel; at least one sealing ring is often arranged on the plunger part 74 for sealing liquid, the tapered rod part 73 is in a tapered shape which increases from the ball end of the plunger to the plunger part 74, and when the plunger 70 moves to a certain position, the tapered rod part 74 is in contact with the inner ring periphery of the plunger hole 81 to play a force transmission role. It should be noted that the plunger 70 is not limited to a tapered plunger type, and may include a rod-plunger with a ball-end or a spherical plunger with a universal joint.

In operation, hydraulic pressure acts on the plunger 70 and is further transmitted to the slide plate 50, and in general, the axial force of the plunger 70 acting on the slide plate 50 is greater than the sum of the supporting force of the swash plate 40 acting on the slide plate 50 through oil film reaction and the return force of the plunger 70, so that the slide plate 50 always slides against the swash plate 40 through a layer of oil film.

Considering that the initial sealing is still needed between the sliding plate and the swash plate when the plunger pump is started to build up the oil pressure as soon as possible, an initial sealing device is needed on the side of the flow distribution sliding plate pair.

Preferably, one of the initial sealing devices, as shown in fig. 20, is provided with a spring preloading device between the sliding plate 50 and the cylinder 80, and the spring preloading device enables a certain initial contact force between the flow distribution sliding plate pair and the flow distribution pair. The spring preloading device comprises a central spring 100, a retainer ring 101 and a spherical hinge 102, wherein the preloading spring force of the central spring 100 acts on the pressure plate 60 through the spherical hinge 102 and is further transmitted to the sliding disc 50, and the other end exerts preloading force on the cylinder end and the port plate 90 through the retainer ring 101.

Preferably, another initial sealing means, as shown in fig. 3 and 4, may also be provided on said sliding plate 50 and/or on the cylinder block 80 with a restraining means having the function of limiting the movement of the sliding plate 50 of said port pair away from the swash plate 40 and of limiting the movement of the cylinder block 80 of said port pair away from the port plate 90.

Further, the restricting means includes a swash plate stopper portion protruding outward on the side of the slide plate 50 close to the slide plate static pressure bearing surface 51, and an engaging means provided on the swash plate bearing stopper portion 41 a. The stopper portion is used for limiting the movement of the third bearing 23, and the engaging means includes an engaging peripheral groove provided on the bearing stopper portion 41a adjacent to the third bearing 23 and a snap spring (not shown) provided on the engaging peripheral groove, which limits the slide plate from being away from the end surface of the swash plate 40 in such a manner as to restrict the outward movement of the third bearing 23.

It is to be expected that an elastic washer (not shown) may also be appropriately provided between the stopper and the third bearing 23 or between the circlip and the third bearing 23, so that the restraining assembly has a certain initial preload to maintain the preloaded state of the slide plate and the swash plate, in addition to restricting the slide plate from moving away from the end face of the swash plate. Similarly, the constraint mode of the engaging device can also be realized by interference fit of the third bearing 23 and the swash plate supporting stop part 41a, and the engaging circumferential groove and the snap spring engaged with the engaging circumferential groove are arranged on the swash plate supporting stop part 41a and adjacent to the third bearing 23 to further constrain. On the cylinder side, the restriction device further comprises a circlip 141 for restricting the cylinder end from moving away from the thrust plate.

Example 2:

as shown in fig. 17, the difference from embodiment 1 is in the variation manner of the variable mechanism, and the structure described in embodiment 1 can be otherwise referred to.

Specifically, the variable mechanism is a motor rotation speed control type variable structure, the variable mechanism includes a controller 163, the controller 163 is a variable frequency controller, the motor rotor assembly 9 includes a rotor core 9a connected to the outer peripheral surface of the drum 11 and a rotor winding 9b embedded in the rotor core 9a, and the motor rotor assembly 9 is controlled by the controller 163 to change the rotation speed, so as to realize a variable output flow rate.

Example 3:

as shown in fig. 19, the difference from the embodiments 1 and 2 is in the variation manner from the variable mechanism, and the other structures can be referred to the structures described in the embodiments 1 and 2.

Specifically, the variable mechanism is a motor rotation speed control type variable structure, the variable mechanism comprises a controller 163 and an encoder 160, the controller 163 is a servo controller, the motor rotor assembly 9 comprises a rotor core 9a connected with the outer circumferential surface of the drum 11 and permanent magnets 9c embedded in the rotor core 9a, and end rings 9d are arranged at two ends of the permanent magnets 9c and used for restraining the permanent magnets from moving axially; main shaft 10 one end is connected with encoder 160, encoder 160 periphery is provided with protection cover 161 in order to prevent that the encoder from receiving damage, dust influence, protection cover 161 passes through bolted connection with front end housing 32, is provided with encoder joint 162 in the protection cover 161 outside, the other end and the encoder 160 lead wire of encoder joint 162 are connected, motor rotor subassembly 9 is in variable rotational speed under the control action of controller 163 to realize variable output flow.

Example 4:

as shown in fig. 21, the difference from embodiments 1, 2 and 3 is in the variation manner of the variable mechanism, and the structure described with reference to the other embodiments can be used.

Specifically, the variable mechanism is a combined variable structure of a swash plate angle control type and a motor rotating speed control type, the variable mechanism comprises a controller 163, the controller 163 comprises a variable frequency type or servo type controller, and the combined variable mechanism can reasonably match working conditions and load changes of the motor according to actual conditions.

Example 5:

as shown in fig. 17, another embodiment of the present invention is shown, which differs from the other embodiments in that an impeller 150 is provided in the end seat 35.

Specifically, an impeller 150 is disposed in the end seat 35 and on the main shaft 10, a plurality of communication holes 36 and an oil inlet hole 38 communicating with the low-pressure port 92 of the port plate 90 are disposed on the end seat 35, the communication holes 36 are circumferentially arranged on the end seat 35, and the impeller 150 is driven by the main shaft 10, so that the low-pressure oil in the housing cavity 34 is accelerated through the communication holes 36, enters the plunger hole 81 through the oil inlet hole 38, and carries away heat.

The structure has the advantages that: firstly, the flow of hot oil in the cavity 34 of the shell is accelerated, so that the hot oil leaves the vicinity of the friction pair as soon as possible, and the influence of high temperature on the friction pair is reduced; and secondly, the side oil suction flow of the sliding disc is improved, and the oil suction performance is enhanced.

Example 6:

as shown in fig. 18, 19 and 21, the main difference from the other embodiments is that the embodiment is a drum-supported electro-hydraulic all-in-one machine, which further includes a fourth bearing 24 and a fifth bearing 25, wherein the fourth bearing 24 and the fifth bearing 25 are respectively interposed between the drum 11 and the housing assembly; in particular, the fourth bearing 24 and the fifth bearing 25 may also be interposed between the drum 11 and the front end cap 32 or the rear end cap 33, respectively, or the fourth bearing 24 may be interposed between the drum 11 and the end seat 35. The motor rotor assembly 9 and the hydraulic assembly are supported on the shell 31 or the end cover 35 through the rotary drum 11, the fourth bearing 24 and the fifth bearing 25 and synchronously rotate, and the plunger 70 reciprocates in a plunger cavity of the cylinder body 80 to realize oil suction and discharge work.

The foregoing is a more detailed description of the present invention that is presented in conjunction with specific preferred embodiments, and is not intended to limit the practice of the invention to those descriptions. For those skilled in the art to which the invention pertains, numerous and varied simplifications or substitutions can be made without departing from the spirit and scope of the invention, and all such modifications and changes as fall within the scope of the claims are intended to be embraced therein.

Claims

1. The utility model provides a compact electricity liquid all-in-one of variable which characterized in that: comprises a hydraulic component, a motor rotor component (9), a motor stator component (8), a rotary drum (11), a shell component and a variable mechanism, the hydraulic assembly comprises a flow distribution sliding disc pair, a flow distribution pair and a plunger pair, the flow distribution pair comprises the end part of a cylinder body (80) and a flow distribution disc (90), the rotating drum (11) is respectively connected with the cylinder body (80) and the motor rotor component (9), so that the rotary drum (11), the cylinder body (80) and the motor rotor component (9) synchronously rotate, the flow distribution sliding disc pair comprises a swash plate (40) and a sliding disc (50) supported on the swash plate (40), the sliding disc (50) is of an integral disc-shaped structure, a static pressure oil film support is formed between the sliding disc (50) and the swash plate (40), the variable mechanism can adjust the output flow, the variable structure comprises a swash plate angle control type variable structure and/or a motor rotating speed control type variable structure.

2. The variable compact electro-hydraulic integrated machine according to claim 1, characterized in that: an end seat (35) is arranged in a shell cavity (34) of the shell assembly, the valve plate (90) is supported on the end seat (35), the valve plate (90) is provided with a low-pressure valve port (92) communicated with a plunger hole (81) of the cylinder body (80), the swash plate (40) is supported on the rear end cover (33), the end seat (35) is provided with an oil inlet hole (38) and an oil inlet groove (37) opening to the shell cavity (34), and the oil inlet hole (38) is respectively communicated with the oil inlet groove (37) of the end seat (35) and the low-pressure valve port (92) of the valve plate (90).

3. The variable compact electro-hydraulic integrated machine according to claim 2, characterized in that: a low-pressure flow distribution window (43) and a high-pressure flow distribution window (44) are arranged on the swash plate (40), the low-pressure flow distribution window (43) and the high-pressure flow distribution window (44) are respectively communicated with an oil inlet (33a) and an oil outlet (33b) which are arranged on the rear end cover (33), the oil inlet (33a) on the rear end cover (33) is provided with an oil way which leads to the low-pressure flow distribution window (43) on the swash plate (40) and an oil way which leads to the shell cavity (34) through an oil inlet fork (33c), when the hydraulic pump works, low-pressure oil enters a plunger hole (81) of a cylinder body (80) from an oil inlet groove (37) of the end seat (35) through a low-pressure flow distribution port (92) of a flow distribution plate (90) and a low-pressure flow distribution window (43) of the swash plate (40) in a double-way manner, and high-pressure oil is discharged from the high-pressure flow distribution window (44) of the swash plate (40) in a single-way, so that the hydraulic oil is sucked and, And (4) discharging.

4. The variable compact electro-hydraulic integrated machine of claim 3, wherein: the variable mechanism is set to be a swash plate angle control type variable structure (110) and comprises variable pistons (111), control valves (112) and variable springs (113), a cylindrical sliding arc surface (45) which is formed into a cylindrical shape is arranged on a supporting surface, opposite to the rear end cover (33), of the swash plate (40), the variable pistons (111) drive the swash plate (40) to slide on the cylindrical sliding arc surface (45), a groove-shaped low-pressure opening (46) and a groove-shaped high-pressure opening (47) which are formed into a groove shape are formed in the cylindrical sliding arc surface (45) of the swash plate (40), and the groove-shaped low-pressure opening (46) and the groove-shaped high-pressure opening (47) are correspondingly communicated with an oil inlet (33a) and an oil outlet (33b) in the rear end cover (33) respectively.

5. The variable compact electro-hydraulic integrated machine according to claim 2, characterized in that: the hydraulic oil sucking and discharging device is characterized in that a high-pressure flow distribution window (44) is arranged on the swash plate (40), the high-pressure flow distribution window (44) is communicated with an oil outlet (33b) formed in the rear end cover (33), an oil inlet (33a) formed in the rear end cover (33) is communicated with a shell cavity (34), all low-pressure oil enters the shell cavity (34) from the oil inlet (33a) formed in the rear end cover (33), when the hydraulic oil sucking and discharging device works, the low-pressure oil in the shell cavity (34) enters a plunger hole (81) of the cylinder body (80) through a low-pressure flow distribution port (92) of the flow distribution plate (90) from an oil inlet groove (37) of the end seat (35) in a one-way mode, and the high-pressure oil is discharged from the high-pressure flow distribution window (44) of the swash plate (40) in a one-way, so that the hydraulic oil is sucked and discharged.

6. The variable compact electro-hydraulic integrated machine of claim 5, wherein: the variable mechanism is set to be a swash plate angle control type variable structure and comprises variable pistons (111), a control valve (112) and a variable spring (113), a bearing surface, opposite to the rear end cover (33), on the swash plate (40) is provided with a cylindrical sliding arc surface (45), the variable pistons (111) drive the swash plate (40) to slide on the cylindrical sliding arc surface (45), a groove-shaped high-pressure port (47) is formed in the cylindrical sliding arc surface (45) of the swash plate (40), and the groove-shaped high-pressure port (47) is correspondingly communicated with the oil outlet (33 b).

7. The variable compact electro-hydraulic integrated machine according to claim 1, characterized in that: the variable mechanism is a motor rotating speed control type variable structure and comprises a controller (163), the controller (163) is a variable frequency controller, the motor rotor assembly (9) comprises a rotor core (9a) connected with the outer peripheral surface of the rotary drum (11) and a rotor winding (9b) embedded in the rotor core (9a), and the rotating speed of the motor rotor assembly (9) is variable under the control action of the controller (163), so that variable output flow is achieved.

8. The variable compact electro-hydraulic integrated machine according to claim 1, characterized in that: the variable mechanism is set to be a motor rotating speed control type variable structure and comprises a controller (163) and an encoder (160), the controller (163) is a servo controller, the motor rotor assembly (9) comprises a rotor core (9a) connected with the outer peripheral surface of the rotary drum (11) and a permanent magnet (9c) embedded in the rotor core (9a), one end of the main shaft (10) is connected with the encoder (160), and the motor rotor assembly (9) can rotate at a variable speed under the control action of the controller (163) so as to achieve variable output flow.

9. The variable compact electrohydraulic all-in-one machine of claim 1, wherein: the variable mechanism is a combined variable structure of a swash plate angle control type and a motor rotating speed control type, the variable mechanism comprises a controller (163), the controller (163) comprises a variable-frequency type or servo type controller, and the combined variable structure can reasonably match working conditions and load changes of the motor according to actual conditions.

10. The variable compact electro-hydraulic integrated machine according to claim 2, characterized in that: an impeller (150) is arranged in the end seat (35) and on the main shaft (10), a plurality of communicating holes (36) and an oil inlet hole (38) of a low-pressure flow distribution port (92) communicated with the flow distribution plate (90) are formed in the end seat (35), and the impeller (150) is driven by the main shaft (10) to accelerate low-pressure oil in the shell cavity (34) to enter the plunger hole (81) through the communicating holes (36) and pass through the oil inlet hole (38) and take away heat.

11. The variable compact electro-hydraulic integrated machine according to any one of claims 1-10, characterized in that: the hydraulic assembly is of a shaft supporting structure and further comprises a first bearing (21) and a second bearing (22), a main shaft axis (10C) of the main shaft (10) is overlapped with a cylinder body axis of a cylinder body (80), one end of the main shaft (10) penetrates through an end seat (35) to a front end cover (32) and is supported on the first bearing (21), the other end of the main shaft (10) penetrates through a rear end cover (33) and is supported on the second bearing (22), the cylinder body (80) is supported on the main shaft (10) and is in key connection with the main shaft (10) to achieve synchronous rotation, the plunger pair comprises a plunger hole wall of the cylinder body (80) and a plunger (70), and the plunger (70) does reciprocating motion in a plunger cavity of the cylinder body (80) to achieve oil suction and discharge work.

12. The variable compact electro-hydraulic integrated machine according to any one of claims 1-10, characterized in that: the hydraulic assembly is of a rotary drum supporting structure and further comprises a fourth bearing (24) and a fifth bearing (25), the fourth bearing (24) and the fifth bearing (25) are respectively clamped between the rotary drum (11) and the shell assembly, the motor rotor assembly (9) and the hydraulic assembly are supported on the shell assembly through the rotary drum (11), the fourth bearing (24) and the fifth bearing (25) and achieve synchronous rotation, the plunger pair comprises a plunger hole wall of the cylinder body (80) and the plunger (70), and the plunger (70) reciprocates in a plunger cavity of the cylinder body (80) to achieve oil suction and discharge work.