CN214660668U - Large-traffic compact electricity liquid all-in-one - Google Patents

Abstract

The utility model discloses a large-traffic compact electricity liquid all-in-one, stator module, rotary drum and the casing subassembly of rotor subassembly, motor including hydraulic pressure subassembly, motor, hydraulic pressure subassembly is vice including the slide plate that joins in marriage a class and the plunger is vice, the plunger is vice including cylinder body and plunger, the rotary drum be connected with the rotor subassembly of motor and with the cylinder body synchronous revolution, the cylinder body holds just be used in the rotary drum the axial hydraulic pressure force of cylinder body is balanced each other or offsets, it includes sloping cam plate and the slide plate of supporting on the sloping cam plate to join in marriage a class slide plate pair, the slide plate is whole disc-shaped structure, form the oil film supporting of static pressure between slide plate and the sloping cam plate. The utility model discloses an electricity liquid all-in-one electricity liquid highly fuses has characteristics such as compact structure, low noise, energy-efficient, high power density, large-traffic, the various convenience of variable, long-life.

Description

Large-traffic compact electricity liquid all-in-one

Technical Field

The utility model belongs to the technical field of power transmission and control, in particular to large-traffic compact electricity liquid all-in-one.

Background

The hydraulic system plays an important role in modern industrial technology, and has absolute advantages particularly in terms of high pressure, high power and quick response. The hydraulic power unit that uses the motor as the prime mover among traditional hydraulic system is mostly that a plurality of dispersed independent parts are connected and forms, as shown in fig. 1, the hydraulic transmission unit contains independent parts such as hydraulic pump 1, motor 2, shaft coupling 3, and 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. Meanwhile, in order to meet the requirements of high-power and high-flow working conditions, the hydraulic pump 1 connected with the high-power motor needs to be connected with two hydraulic pumps in series to meet the requirements. The structure has the problems of complex structure, large occupied volume, low power density, low efficiency, large assembly error, large noise, 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 two hydraulic pumps 2 and the coupling 3 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 and ships. 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) 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.

(5) 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.

SUMMERY OF THE UTILITY MODEL

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

The utility model discloses technical scheme implementation of technique: a large-traffic compact electricity liquid all-in-one which characterized in that: the hydraulic assembly comprises a flow distribution sliding disc pair and a plunger pair, the plunger pair comprises a cylinder body and a plunger, the rotor is connected with the rotor assembly of the motor and synchronously rotates with the cylinder body, the cylinder body is accommodated in the rotor, axial hydraulic pressure acting on the cylinder body is balanced or offset, 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, and a static pressure oil film support is formed between the sliding disc and the swash plate.

Large-traffic compact electricity liquid all-in-one, it the cylinder body is two split type independent cylinder body structures that the opposition was arranged on the main shaft, the cylinder body has a plurality of plunger holes with cylinder body center axle center hoop evenly distributed, the plunger hole of cylinder body is one end and seals, one end open-ended blind hole structure, and wherein the cylinder body terminal surface on one side of mutual opposition seals.

Large-traffic compact electricity liquid all-in-one, it main shaft middle part circumference is provided with outside convex main shaft connecting portion, rotary drum middle part circumference is provided with inside convex rotary drum connecting portion, the rotary drum is connected with the rotor subassembly of main shaft and motor respectively, makes the rotor subassembly synchronous revolution of rotary drum, main shaft, cylinder body and motor, the cylinder body tip butt of opposition and closed one side is at the both ends of main shaft connecting portion for the axial hydraulic pressure force that acts on two cylinder body tip is balanced each other.

Large-traffic compact electricity liquid all-in-one, it the cylinder body is monolithic structure, the cylinder body both ends have a plurality of plunger holes that use cylinder body center axle center hoop evenly distributed, the plunger hole of cylinder body is both ends open-ended through-hole structure, the rotary drum is connected with the rotor subassembly of cylinder body and motor respectively, makes the rotor subassembly synchronous revolution of rotary drum, cylinder body and motor.

Large-traffic compact electricity liquid all-in-one, it is vice for two-way high-low pressure distribution sliding tray that the distribution sliding tray is vice, the sloping cam plate supporting in the distribution sliding tray is on the front end housing and the rear end cap of casing subassembly, be provided with low pressure distribution window and high pressure distribution window on the sloping cam plate.

Large-traffic compact electricity liquid all-in-one, it variable mechanism sets up to sloping cam plate angle control formula variable structure, variable mechanism includes variable piston, control valve and variable spring, have on the sloping cam plate and the bearing surface of front end housing and rear end housing opposition and take shape to the smooth cambered surface of columniform cylinder, the variable piston orders about the sloping cam plate is in slide on the smooth cambered surface of cylinder, the smooth cambered surface of cylinder of sloping cam plate has configuration for flute profile low pressure port and flute profile high-pressure port of flute profile, flute profile low pressure port and flute profile high-pressure port correspond the intercommunication with oil inlet and oil-out on front end housing and the rear end housing respectively.

The utility model discloses a large-traffic compact electricity liquid all-in-one, its the variable mechanism sets up to motor rotational speed control formula variable structure, the variable mechanism includes the controller, the controller is the inverter controller, the rotor subassembly of motor includes the rotor core that is connected with the rotary drum outer peripheral face and the rotor winding nested in the rotor core, the rotor subassembly of motor is in the variable rotational speed under the control of controller to realize variable flow output;

or the controller is a servo controller, the rotor assembly of the motor comprises a rotor iron core connected with the peripheral surface of the rotary drum and a permanent magnet embedded in the rotor iron core, one end of the main shaft is connected with the encoder, and the rotor assembly of the motor can change the rotating speed under the control action of the controller, so that variable flow output is realized.

Large-traffic compact electricity liquid all-in-one, it variable mechanism sets up to swash plate angle control formula and motor speed control formula joint variable structure, variable mechanism includes the controller, the controller includes inverter type or servo controller, joint variable mechanism can make it rationally match distribution motor operating mode and load change according to actual conditions.

Large-traffic compact electricity liquid all-in-one, it is provided with casing oil inlet and casing oil-out on casing assembly's the casing, casing oil inlet and casing oil-out communicate with low pressure flow distribution window and high pressure flow distribution window that sets up on casing assembly oil feed oil duct and oil outlet duct and sloping cam plate respectively.

Large-traffic compact electricity liquid all-in-one, it hydraulic pressure unit is hydraulic pressure pump unit, the motor is the motor, the rotor subassembly of motor drives cylinder body and rotary drum synchronous revolution under the electromagnetic force effect, reciprocating motion in the cylinder body is followed to the plunger, hydraulic pressure pump unit output high pressure fluid, electric energy transformation becomes mechanical energy and further turns into the hydraulic pressure ability.

Large-traffic compact electricity liquid all-in-one, it hydraulic pressure subassembly is the hydraulic motor subassembly, the motor is the generator, and in outside high-pressure fluid input electricity liquid all-in-one, hydraulic pressure can drive the hydraulic motor rotation to the rotor subassembly synchronous revolution that drives rotary drum and motor, the motor is in the electricity generation mode, and hydraulic pressure can turn into mechanical energy and further turn into the electric energy.

Large-traffic compact electricity liquid all-in-one, it hydraulic assembly is axle support formula structure, and it still includes first bearing and second bearing, the main shaft axle center of main shaft and the coincidence of the cylinder body axle center of cylinder body, main shaft one end is run through the vice front end housing of joining in marriage a class sliding tray and is supported on first bearing, and the other end runs through the vice rear end housing of joining in marriage a class sliding tray and supports on the second bearing, the cylinder body supporting is in main shaft and realizes synchronous rotation through the key-type connection with the main shaft, reciprocating motion is done at the plunger intracavity of cylinder body to the plunger, realizes oil absorption work.

Large-traffic compact electricity liquid all-in-one, it hydraulic component is rotary drum supporting formula structure, and it still includes fourth bearing and fifth bearing, fourth bearing and fifth bearing press from both sides respectively and establish between rotary drum and casing assembly, the rotor subassembly of motor passes through rotary drum and fourth bearing and fifth bearing support with the cylinder body and realizes synchronous revolution on casing assembly, reciprocating motion is done at the plunger intracavity of cylinder body to the plunger, realizes inhaling oil extraction work.

Based on the technical scheme, the beneficial effects of the utility model are that:

(1) the utility model discloses a small, power density is high. Traditional hydraulic power unit, independent parts such as motor, two hydraulic pumps, shaft coupling are arranged to the axial, and axial length is long, and occupation space is big, and the utility model provides an electricity liquid all-in-one, axial length reduces more than 60%, and occupation space reduces more than 60%, and the motor highly fuses into an organic whole with the hydraulic pump, and holistic power density is big, especially is suitable for in the occasion that space is limited, that requirement power density is big such as engineering machine tool, electric automobile, robot, aerospace, naval vessel.

(2) The utility model discloses a discharge capacity is big. The utility model discloses establish ties two hydraulic assembly and be integrated together, common integrated in the casing subassembly of motor, in the same casing space, realize the output of double high-pressure fluid, can satisfy big discharge capacity, high pressure, high-power operating mode requirement.

(3) The axial hydraulic pressure of the utility model is balanced each other. The utility model discloses with the cylinder body opposition or set to overall structure, axial force is balanced each other or offsets for the epaxial bearing of electricity liquid all-in-one main shaft does not receive self axial hydraulic pressure force effect, is favorable to bearing life's improvement.

(4) The utility model discloses a variable is convenient. The utility model discloses in the slide plate pair that flows that adopts, its structure will flow, the variable slope, the static pressure supporting function is integrated in the slide plate pair that flows, adopts current optimal terminal surface oil film supporting mode between slide plate and the sloping cam plate and have the function of flowing concurrently, still can realize through modes such as the slope mode or the motor variable speed that change the sloping cam plate simultaneously, realize that the variable is various convenient.

(5) The utility model discloses an it is efficient. The motor and the hydraulic pump are highly integrated, so that connecting parts such as a coupler and an air cooling device are omitted, the links of energy conversion and power transmission and the additional energy loss of the air cooling device are reduced, and the mechanical friction loss, the pipeline pressure loss, the leakage loss and the like are greatly reduced.

(6) The utility model discloses noise and vibration have been showing and have been reduced. 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 utility model provides an electricity liquid all-in-one highly fuses integratively, and motor, hydraulic pump are coaxial, the shell altogether, have cancelled shaft coupling, air cooling device, connecting line, the influence of above three to noise and vibration of eliminating fundamentally, and the noise is showing and is reducing.

(7) The utility model discloses a longe-lived, the reliability is high. The electro-hydraulic integrated machine is highly integrated, and all mechanical parts are highly integrated, thereby simplifying the structural complexity; the sliding plate in the flow distribution sliding plate pair is of an integral structure, the plunger in the plunger pair is of a conical structure, the unique design of the sliding plate and the plunger 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, larger flow and longer service life.

(8) The utility model discloses the external leakage has been reduced. 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.

(9) The utility model discloses highly agree with future industrial technology development trend. The utility model provides an electricity liquid all-in-one highly fuses accords with future industrial technology development requirement, to environmental protection and energy saving, integrate, digital, intelligent orientation development promptly.

Drawings

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

Fig. 2 is the structure schematic diagram of the electro-hydraulic integrated machine of the utility model.

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

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

Fig. 5 is a plan view of one end of the middle slide plate of the present invention.

Fig. 6 is a B-B sectional view of the sliding plate structure shown in fig. 5 according to the present invention.

Fig. 7 is a plan view of the other end of the middle sliding plate of the present invention.

Fig. 8 is a plan view of an end bearing surface of the swash plate of the present invention.

Fig. 9 is a plan view of the bearing surface of the other end of the swash plate according to the present invention.

Fig. 10 is a cross-sectional view of the drum of the present invention along the axis.

Fig. 11 is a plan view of one side of the drum of the present invention.

Fig. 12 is an embodiment of the integrated electro-hydraulic integrated machine of the middle cylinder body of the present invention.

Fig. 13 is an embodiment of the present invention, which is a swash plate angle control type electro-hydraulic all-in-one machine.

Fig. 14 is an embodiment of the present invention, which is a variable frequency control type electro-hydraulic all-in-one machine.

Fig. 15 is an embodiment of the servo control type electro-hydraulic all-in-one machine of the present invention.

Fig. 16 is an embodiment of the electro-hydraulic integrated machine with the oil replenishing pump of the present invention.

Fig. 17 shows an embodiment of the middle drum supporting variable electrohydraulic all-in-one machine of the present invention.

Fig. 18 is a cross-sectional view taken along line a-a of fig. 17 according to the present invention.

FIG. 19 shows an electro-hydraulic integrated machine of the present invention with a middle rotary drum supporting type quantitative slide plate inner supporting mode

Fig. 20 is an embodiment of the electro-hydraulic integrated machine for oil inlet and outlet of the middle casing of the present 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 stator component of the motor, 8a is a stator core, 8b is a stator winding, 9 is a rotor component of the motor, 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, 10a is a main shaft connecting part, 10C is a main shaft axis, 11 is a rotary drum, 12 is a rotary drum connecting part, 13 is an oil passing hole, 14 is a rotary drum connecting key, 15 is a bulge, 16 is a first stop, 17 is a second stop, 18 is a connecting pin, 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, 26 is an oil supplementing pump, 31 is a shell, 31a shell oil inlet, 31b is a shell oil outlet, 31C is a shell oil inlet, 31d is a shell oil outlet passage, 32 is a front end cover, 32a is a front end cover oil inlet, 32b is a front end cover oil outlet, 32C is a front end cover oil inlet passage, 32d is a front end cover oil outlet passage, 33 is a rear end cover, 33a is a rear end cover oil inlet, 33b is a rear end cover oil outlet, 33C is a rear end cover oil inlet passage, 33d is a rear end cover oil outlet passage, 34 is a shell cavity, 40 is a swash plate, 41 is a swash plate bearing surface, 41a is a bearing 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, 49 is a shaft pin, 50 is a sliding plate, 50C is a sliding plate shaft center, 51 is a sliding plate static pressure bearing surface, 52 is a sliding plate boss surface, 53 is a sliding plate waist-shaped hole, 54 is a sliding plate external sealing portion, 55 is a sliding plate internal sealing portion, 56 is a sliding plate interval 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 part, 74 is a plunger part, 80 is a cylinder body, 81 is a plunger hole, 100 is a center 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 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 embodiments of the present invention are shown in a typical orientation such that when the central axis of the main shaft of the electrohydraulic all-in-one machine 5 is at a horizontal rest, the front end cap 32 side is left, the rear end cap 33 is right, and the terms "longitudinal", "lateral", "up", "down", "front", "rear", "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, it is not intended to indicate or imply that the device or component referred to must have a particular orientation, and that it is to be understood that the device may be manufactured, stored, transported, used, and sold in an orientation other than the position described.

Example 1:

as shown in fig. 2 to 11, in the preferred embodiment of the electro-hydraulic integrated machine 5 of the present invention, in the shown preferred embodiment, the electro-hydraulic integrated machine 5 is a shaft support structure, the electro-hydraulic integrated machine 5 includes a hydraulic component, a rotor component 9 of a motor, a stator component 8 of the motor, a rotating drum 11, a housing component, a main shaft 10, a first bearing 21 and a second bearing 22, the hydraulic component includes a plunger pair and a flow distribution sliding plate pair, the plunger pair includes a plunger 70 and a cylinder 80, preferably, the plunger 70 is a conical structure with a central large hole arranged 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. A main shaft axis 10C of the main shaft 10 coincides with a cylinder body axis of a cylinder body 80, one end of the main shaft 10 penetrates through the flow distribution sliding disc pair to the front end cover 32 and is supported on the first bearing 21, the other end penetrates through the flow distribution sliding disc pair to the rear end cover 33 and is supported on the second bearing 22, and the cylinder body 80 is supported on the main shaft 10 and is in key connection with the main shaft 10; the rotor assembly 9 of rotary drum 11 and motor be connected and with cylinder body 80 synchronous revolution, cylinder body 80 holds in the rotary drum 11 and be in the effect axial hydraulic pressure of cylinder body 80 is balanced each other or offsets, plunger 70 is reciprocating motion in the plunger intracavity of cylinder body 80, realizes inhaling oil extraction work, the electricity-liquid all-in-one machine outputs high-pressure fluid, and the electricity-liquid all-in-one machine realizes converting into mechanical energy and further converting into the hydraulic energy process from the electric energy.

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 stator assembly 8 of the motor includes a stator core 8a, a stator winding 8b, and the like, wherein the stator core 8a is a component of a magnetic circuit of the motor and is formed by punching and laminating a thin silicon steel sheet coated with insulating paint on a surface, an outer peripheral surface of the stator core 8a is fixedly connected with a housing 31 of the housing assembly, a plurality of notches (not shown) are formed in an inner peripheral surface of the stator core 8a, 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 a wire outlet end of the stator winding 8b is led to a wire outlet box 6 arranged on the housing 31.

Specifically, the rotor assembly 9 of the motor includes a rotor core 9a, a rotor winding 9b, and the like, wherein the rotor core 9a is also a component of a magnetic circuit of the motor, and is also formed by punching and laminating a thin silicon steel sheet coated with an insulating varnish on a surface, an inner circumferential surface of the thin silicon steel sheet is fixedly connected to a drum 11, side surfaces of both sides of the rotor core 9a abut against a protruding portion 15 of the drum 11 through a first stopper 16 to limit axial displacement of the rotor core 9a and the drum 11, an 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 an induced current, the rotor winding 9b includes, but is not limited to, a squirrel-cage structure and a winding-type structure rotor winding, wherein a copper bar or an aluminum bar is inserted into a groove on the rotor core 9a as a guide bar, and the two ends are connected by a copper ring or an aluminum ring to form a cage-shaped structure.

A certain air gap is kept between the stator assembly 8 of the motor and the rotor assembly 9 of the motor, 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 stator assembly 8 and rotor assembly 9 of the electric machine.

Specifically, the cylinder 80 is a split type independent cylinder structure which is arranged oppositely on the main shaft 10, the cylinder 80 has a cylindrical configuration with a circular cross section along the radial direction and is accommodated in the cavity of the rotary drum 11, the cylinder 80 has a plurality of plunger holes 81 which are circumferentially and uniformly distributed around the center axis of the cylinder and a main shaft assembling hole which is used for accommodating the main shaft 10 at the center, and the plunger holes 81 of the cylinder 80 are of a structure with one closed end and one open end. Preferably, the number of the plunger holes 81 is generally set to 7 or 9. The main shaft 10 passes through a main shaft assembly hole of the cylinder block 80 and is connected to the cylinder block 80 in such a manner that a connection key is provided on the outer circumferential surface of the shaft body, and the cylinder block 80 is supported on the main shaft 10 in such a manner that it moves synchronously with the main shaft 10.

It should be noted that the end of the cylinder 80 is not provided with a port plate abutting against it, thus reducing a friction pair and improving the volumetric efficiency thereof; because the end part of the cylinder body 80 is not abutted to the valve plate, the end part of the cylinder body does not need to be precisely machined, and the manufacturing and using cost is reduced; the end part of the cylinder body 80 is not provided with a port plate, and even if partial lateral force exists, the problems of failure and the like caused by eccentric wear can be avoided.

Specifically, the outer peripheral surface of the drum 11 is connected with a rotor assembly 9 of a motor, a drum connecting portion 12 extending inward is arranged inside the drum 11, a plurality of oil passing holes 13 are arranged in the circumferential direction of the drum connecting portion 12, and the oil passing holes 13 communicate with the housing cavities 34 on both sides to balance oil pressure on both sides. Furthermore, the drum 11 is provided with a restraining device for restraining the axial movement, and the restraining device includes a protruding portion 15 protruding outwards on both sides of the drum 11 for restraining the axial displacement of the motor rotor, and a first stopper 16 interposed between the motor rotor and the protruding portion 15.

Specifically, the main shaft 10 is circumferentially provided with a main shaft connecting portion 10a protruding outward in the middle, the main shaft connecting portion 10a is sandwiched between the two cylinders 80, and the cylinder ends opposite to each other and on the closed side abut against the two ends of the main shaft connecting portion 10a, so that axial hydraulic forces acting on the two cylinder ends are balanced with each other. The spindle connecting part 10a of the spindle 10 is connected with the boss 15 of the drum 11, and the connection includes but is not limited to one or a combination of key connection, bolt or connecting pin 18 connection, interference fit connection, and the like. The main shaft 10 is supported on a first bearing 21 and a second bearing 22, the first bearing 21 including but not limited to a radial deep groove ball bearing, a roller bearing, a radial thrust ball bearing or a tapered roller bearing. When the pump works, the rotor assembly of the motor is driven to rotate by the electromagnetic force, the cylinder body 80 is further driven to rotate synchronously by the main shaft 10, the end parts of the cylinder bodies 80 at two sides abut against the main shaft connecting part 10a under the action of axial hydraulic force, the axial hydraulic force is mutually counteracted, and radial force is born by the first bearing 21 and the second bearing 22 which are supported at two ends of the main shaft 10.

Specifically, the flow distribution sliding disc pair comprises a sliding disc 50 and a swash plate 40 supported on a front end cover 32 and 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, one end of the sliding disc 50 is provided with a plurality of sliding disc waist-shaped holes 53, the other end face of the sliding disc 50 is provided with a plurality of plunger ball sockets 58, the sliding disc waist-shaped holes 53 on the sliding disc 50 penetrate through the plunger ball sockets 58, and the swash plate 40 is provided with a flow distribution oil groove 42 communicated with a rear end cover oil inlet 33a and a rear end cover oil outlet 33b on the rear end cover 33. Further, as shown in fig. 8, the swash plate 40 and the slide plate 50 are provided with a low pressure port window 43 and a high pressure port window 44 which are separated.

As shown in fig. 3 and 4, the housing assembly of the electro-hydraulic integrated 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 a rotor assembly 9 of the motor, a stator assembly 8 of the motor, and a 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, the front end cover 32 is provided with a front end cover oil inlet 32a and a front end cover oil outlet 32b, the rear end cover 33 is provided with a rear end cover oil inlet 33a and a rear end cover oil outlet 33b, and the low-pressure flow distribution window 43 and the high-pressure flow distribution window 44 are respectively communicated with the oil inlet and the oil outlet of the front and rear end covers.

Specifically, the plunger pair includes a plunger 70 and a cylinder 80, the plunger 70 is of a conical structure, and the plunger is provided with a large-aperture plunger center hole 72 which is used for oil inlet and outlet and communicates a plunger ball socket 58 and a plunger hole 81.

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. 5, 6 and 7, 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.

Further, as shown in fig. 6, 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 waist-shaped holes 53 having a waist shape are provided on the swash plate static pressure bearing surface 51, preferably, the swash plate waist-shaped 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 waist-shaped holes 53 are communicated to the 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.

More 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 the plunger hole 81 and 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 plunger hole wall of the cylinder 80 and is reciprocatable therein, and the plunger ball 71 is supported by the plunger ball socket 58 of the slide plate 50 in a spherical shape and is slidable; 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 is gradually increased 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 73 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.

From the above analysis, it can be known that the structure has the characteristics of large flow, 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, and independent components such as a motor 1, two hydraulic pumps 2, a coupler 3 and the like are axially arranged, and the hydraulic power unit has a long axial length and a large occupied space, fig. 2 is the electro-hydraulic integrated machine of the utility model, wherein the axial length is reduced by more than 60%, the occupied space is reduced by more than 50%, the motor and the hydraulic pumps are highly integrated into a whole, and the whole power density is large, so that the hydraulic power unit is particularly suitable for application occasions where the space is limited, the required power density is large, such as engineering machinery, electric automobiles, robots, aerospace, ships and the like, and the required power density is large and the application occasions with high power and large flow are required; 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.

When the spindle works, hydraulic pressure acts on the end part of the cylinder body at one end of the cylinder body, and the end parts of the two cylinder bodies are abutted against the convex connecting part of the spindle, so that the axial hydraulic pressure is balanced and offset mutually, and the spindle is basically free from the action of the hydraulic pressure.

In operation, at one end of the flow distribution sliding disc pair, hydraulic pressure acts on the plunger 70 and is further transmitted to the sliding disc 50, and generally, the axial force of the plunger 70 acting on the sliding disc 50 is greater than the sum of the supporting force of the swash plate 40 acting on the sliding disc 50 through oil film reaction and the return force of the plunger 70, so that the sliding disc 50 always abuts against the swash plate 40 through a layer of oil film to slide.

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. 14, 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 pre-tightening device comprises a central spring 100, a retainer ring 101 and a spherical hinge 102, wherein one end of the pre-tightening 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 plate 50, and the other end of the pre-tightening spring force acts on the end part of the cylinder body through the retainer ring 101.

Preferably, another initial sealing device, as shown in fig. 3 and 4, may also be provided on the sliding plate 50 and/or the cylinder block 80 with a restriction device having a function of restricting the sliding plate 50 of the port sliding plate pair from moving away from the swash plate 40 and restricting the cylinder block 80 from moving away from the main shaft connecting portion 10 a.

Further, the restricting means includes a swash plate stopper portion protruding outward on the side of the slide plate 50 close to the static pressure bearing surface 51 of the slide plate for restricting the movement of the third bearing 23, and a snap-fit means provided on the swash plate bearing stopper portion 41a and including a snap-fit circumferential groove provided on the bearing stopper portion 41a adjacent to the third bearing 23 and a snap spring (not shown) provided on the snap-fit circumferential groove for restricting the outward movement of the third bearing 23 away from the end surface of the swash plate 40.

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 supporting stop portion 41a of the swash plate, which is adjacent to the third bearing 23, is provided with a circumferential engaging groove and a snap spring engaged with the circumferential engaging groove to perform a further constraint action. 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. 13, 14, 15, 17 and 18, the difference from embodiment 1 is that the electrohydraulic single-body machine is provided with a variable mechanism, and the other structure can be referred to embodiment 1.

In a preferred embodiment, as shown in fig. 13, the variable mechanism is a swash plate angle controlled variable structure 110, the swash plate angle controlled variable structure 110 includes variable pistons 111, a control valve 112 and a variable spring 113, the control valve 112 is connected to the rear end cover 33, a plurality of fluid passages are disposed 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 swash plate angle, the control valve 112 can be set to a plurality of variable control modes including, but not limited to, a constant pressure mode, a constant flow rate mode, a constant power mode, 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 and correspondingly communicated with a rear end cover oil inlet 33a and a rear end cover oil outlet 33b on the rear end cover 33.

In another preferred embodiment, as shown in fig. 14, the variable mechanism is a variable mechanism with a motor speed control type, the variable mechanism includes a controller 163, the controller 163 is a variable frequency controller, the rotor assembly 9 of the motor includes a rotor core 9a connected to the outer circumferential surface of the drum 11 and a rotor winding 9b embedded in the rotor core 9a, and the rotor assembly 9 of the motor can change the speed under the control of the controller 163, thereby realizing a variable output flow rate.

In another preferred embodiment, as shown in fig. 15, the variable mechanism is configured as a motor speed control type variable mechanism, the variable mechanism includes a controller 163 and an encoder 160, the controller 163 is a servo controller, the rotor assembly 9 of the motor includes a rotor core 9a connected to the outer circumferential surface of the drum 11 and a permanent magnet 9c nested in the rotor core 9a, and end rings 9d are provided at two ends of the permanent magnet 9c for restraining the permanent magnet 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 the protection cover 161 outside is provided with encoder joint 162, the encoder joint 162 other end and encoder 160 pin connection, the rotor subassembly 9 of motor is in variable rotational speed under the control action of controller 163 to realize changeable output flow.

It is anticipated that in another preferred embodiment, the variable mechanism is configured as a combined variable structure of swash plate angle control and motor speed control, 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 the working condition and the load change of the motor according to the actual situation.

Example 3:

as shown in fig. 16, another embodiment of the present invention is shown, which is different from the other embodiments in that an oil replenishing pump 26 is provided at the end of the main shaft 10.

In the illustrated embodiment, an oil replenishing pump 26 is connected to an end of the main shaft 10, and the oil replenishing pump 26 is used for supplying oil to a hydraulic system or providing hydraulic operating force; the oil replenishing pump 26 is connected with the front end cover 32 and the rear end cover 33 through bolts, and the external oil replenishing pump 26 can be a gear pump or a vane pump and the like.

Example 4:

as shown in fig. 17, 18 and 19, 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. The rotor assembly 9 and the hydraulic assembly of the motor are supported on the shell assembly 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.

Example 5:

as shown in fig. 19, the main difference from the other embodiments is that the supporting manner of the sliding disk in this embodiment is the supporting manner in the bearing.

In the preferred embodiment shown, the hydrostatic bearing surface 51 of the sliding plate 50 is supported on the swash plate 40 and is tightly fitted to the working surface of the swash plate 40, a support shaft or a support shaft pin 49 extending outward is provided in the center of the swash plate 40, a third bearing 23 is interposed between the swash plate support shaft or the support shaft pin 49 and the inner side of the sliding plate 50, the sliding plate 50 is supported on the third bearing 23 in a radially constrained state, the third bearing 23 may be provided as one of, but not limited to, a radial ball bearing, a needle bearing, a cylindrical roller bearing, a tapered roller bearing, and a radial ball bearing, and the plunger 70 reciprocates in a plunger cavity of the cylinder 80 during the rotation of the spindle 10 and the cylinder 80, thereby performing the oil suction and discharge operation of the pump or the motor. In the implementation, the radial size of the motor rotor can be smaller by adopting the inner support, which is beneficial to improving the rotating speed.

Example 6:

as shown in fig. 20, the main difference from the other embodiments is the number and the manner of the oil inlet and the oil outlet in the embodiment.

In the illustrated preferred embodiment, the housing 31 is provided with a housing oil inlet 31a, a housing oil outlet 31b, a housing oil inlet oil passage 31c and a housing oil outlet oil passage 31d, the front end cover 32 is provided with a front end cover oil inlet oil passage 32c and a front end cover oil outlet oil passage 32d, the rear end cover 33 is provided with a rear end cover oil inlet oil passage 33c and a rear end cover oil outlet oil passage 33d, the housing oil inlet oil passage 31c is respectively communicated with the oil inlet and the front end cover oil inlet oil passage 32c and the rear end cover oil inlet oil passage 33c on the front end cover and the rear end cover oil passage 33c, the housing oil outlet oil passage 31d is respectively communicated with the oil outlet and the front end cover oil outlet oil passage 32d and the rear end cover oil outlet oil passage 33d on the front end cover and the rear end cover, and the housing oil inlet 31a and the housing oil outlet 31b are respectively communicated with the low-pressure flow distribution window 43 and the high-pressure flow distribution window 44 on the swash plate 40.

Example 7:

the main difference with the other embodiments is the energy conversion in this embodiment.

Specifically, the electro-hydraulic integrated machine can convert energy reversely, wherein the hydraulic component is a motor hydraulic component, the motor is a generator, external high-pressure oil is input into the electro-hydraulic integrated machine 5, hydraulic energy drives the hydraulic motor to rotate and drives the cylinder body 80, the rotary drum 11 and the rotor component 9 of the motor to rotate synchronously, the motor is in a power generation mode, and the hydraulic energy is converted into mechanical energy and further converted into electric energy. The structure is particularly suitable for the fields of wind power generation and the like.

The above description is further detailed in connection with specific preferred embodiments of the invention and should not be taken as limiting the invention to the specific embodiments described. To those skilled in the art to which the invention pertains, without departing from the spirit of the invention, several simple deductions or replacements can be made, and all the technical solutions and modifications thereof that do not depart from the spirit and scope of the invention should be covered by the scope of the claims of the invention.

Claims (13)

1. A large-traffic compact electricity liquid all-in-one which characterized in that: the hydraulic assembly comprises a flow distribution sliding disc pair and a plunger pair, the plunger pair comprises a cylinder body (80) and a plunger (70), the rotating drum (11) is connected with the rotor assembly (9) of the motor and synchronously rotates with the cylinder body (80), the cylinder body (80) is accommodated in the rotating drum (11) and axial hydraulic pressure acting on the cylinder body (80) is balanced or offset mutually, 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, and a static pressure oil film support is formed between the sliding disc (50) and the swash plate (40).

2. The high-flow compact electro-hydraulic integrated machine according to claim 1, characterized in that: the cylinder body (80) is of two split type independent cylinder body structures which are arranged on the main shaft (10) in an opposite mode, the cylinder body (80) is provided with a plurality of plunger holes (81) which are circumferentially and uniformly distributed around the center axis of the cylinder body, the plunger holes (81) of the cylinder body (80) are of a blind hole structure with one closed end and one open end, and the end faces of the cylinder body (80) on the opposite sides are closed.

3. The high-flow compact electro-hydraulic integrated machine according to claim 2, characterized in that: the hydraulic cylinder is characterized in that a main shaft connecting part (10a) protruding outwards is arranged in the middle of the main shaft (10) in the circumferential direction, a rotary cylinder connecting part (12) protruding inwards is arranged in the middle of the rotary cylinder (11) in the circumferential direction, the rotary cylinder (11) is respectively connected with the main shaft (10) and a rotor assembly (9) of the motor, so that the rotary cylinder (11), the main shaft (10), the cylinder body (80) and the rotor assembly (9) of the motor rotate synchronously, the cylinder body end parts which are opposite to each other and close to one side abut against the two ends of the main shaft connecting part (10a), and axial hydraulic pressures acting on the two cylinder body end parts are balanced with each other.

4. The high-flow compact electro-hydraulic integrated machine according to claim 1, characterized in that: the cylinder body (80) is of an integral structure, a plurality of plunger holes (81) which are circumferentially and uniformly distributed around the center axis of the cylinder body are formed in the two ends of the cylinder body (80), the plunger holes (81) of the cylinder body (80) are of a through hole structure with openings in the two ends, and the rotary drum (11) is respectively connected with the cylinder body (80) and a rotor assembly (9) of the motor, so that the rotary drum (11), the cylinder body (80) and the rotor assembly (9) of the motor synchronously rotate.

5. The high-flow compact electro-hydraulic integrated machine according to claim 1, characterized in that: the flow distribution sliding disc pair is a bidirectional high-pressure and low-pressure flow distribution sliding disc pair, a swash plate (40) in the flow distribution sliding disc pair is supported on a front end cover (32) and a rear end cover (33) of the shell assembly, and a low-pressure flow distribution window (43) and a high-pressure flow distribution window (44) are arranged on the swash plate (40).

6. The high-flow compact electro-hydraulic integrated machine according to claim 5, characterized in that: the electro-hydraulic integrated machine is provided with a variable mechanism, the variable mechanism is a swash plate angle control type variable structure and comprises variable pistons (111), a control valve (112) and a variable spring (113), bearing surfaces, opposite to a front end cover (32) and a rear end cover (33), on a swash plate (40) are provided with cylindrical sliding arc surfaces (45), the variable pistons (111) drive the swash plate (40) to slide on the cylindrical sliding arc surfaces (45), grooved low-pressure ports (46) and grooved high-pressure ports (47) which are in groove shapes are formed in the cylindrical sliding arc surfaces (45) of the swash plate (40), and the grooved low-pressure ports (46) and the grooved high-pressure ports (47) are respectively communicated with oil inlets and oil outlets in the front end cover (32) and the rear end cover (33) correspondingly.

7. The high-flow compact electro-hydraulic integrated machine according to claim 5, characterized in that: the electro-hydraulic integrated machine is provided with a variable mechanism, the variable mechanism is set to be a motor rotating speed control type variable structure and comprises a controller (163), the controller (163) is a variable frequency type controller, a rotor assembly (9) of the motor comprises a rotor core (9a) connected with the outer peripheral surface of a rotating drum (11) and a rotor winding (9b) embedded in the rotor core (9a), and the rotating speed of the rotor assembly (9) of the motor is variable under the control action of the controller (163), so that variable flow output is realized;

or, the controller (163) is a servo controller, the rotor assembly (9) of the motor 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 rotor assembly (9) of the motor can change the rotating speed under the control action of the controller (163) so as to realize variable flow output.

8. The high-flow compact electro-hydraulic integrated machine according to claim 5, characterized in that: the electro-hydraulic integrated machine is provided with a variable mechanism, 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.

9. The high-flow compact electro-hydraulic integrated machine according to claim 1, characterized in that: a shell oil inlet (31a) and a shell oil outlet (31b) are formed in a shell (31) of the shell assembly, and the shell oil inlet (31a) and the shell oil outlet (31b) are respectively communicated with an oil inlet duct and an oil outlet duct which are formed in the shell assembly and a low-pressure flow distribution window (43) and a high-pressure flow distribution window (44) in a swash plate (40).

10. The high-flow compact electro-hydraulic integrated machine according to claim 1, characterized in that: the hydraulic component is a hydraulic pump component, the motor is an electric motor, a rotor component (9) of the electric motor drives a cylinder body (80) and a rotary drum (11) to synchronously rotate under the action of electromagnetic force, the plunger (70) reciprocates in the cylinder body (80), the hydraulic pump component outputs high-pressure oil, and electric energy is converted into mechanical energy and further converted into hydraulic energy.

11. The high-flow compact electro-hydraulic integrated machine according to claim 1, characterized in that: the hydraulic component is a hydraulic motor component, the motor is a generator, external high-pressure oil is input into the electro-hydraulic integrated machine (5), hydraulic energy drives the hydraulic motor to rotate and drives the rotary drum (11) and the rotor component (9) of the motor to synchronously rotate, the motor is in a power generation mode, and the hydraulic energy is converted into mechanical energy and further into electric energy.

12. The mass flow compact electro-hydraulic integrated machine according to any one of claims 1-11, characterized in that: the hydraulic assembly is of a shaft supporting structure and further comprises a first bearing (21) and a second bearing (22), the cylinder body axis of a cylinder body (80) is overlapped with the main shaft axis (10C) of the main shaft (10), one end of the main shaft (10) penetrates through a flow distribution sliding disc pair 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 flow distribution sliding disc pair to 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 connected with the main shaft (10) through a key to realize synchronous rotation, and the plunger (70) reciprocates in a plunger cavity of the cylinder body (80) to realize oil suction and discharge work.

13. The mass flow compact electro-hydraulic integrated machine according to any one of claims 1-11, 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, a rotor assembly (9) and a cylinder body (80) of the motor are supported on the shell assembly through the rotary drum (11), the fourth bearing (24) and the fifth bearing (25) and achieve synchronous rotation, and the plunger (70) reciprocates in a plunger cavity of the cylinder body (80) to achieve oil suction and discharge work.

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