CN114687974A

CN114687974A - Compact type electro-hydraulic integrated machine

Info

Publication number: CN114687974A
Application number: CN202011634128.5A
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 compact type electro-hydraulic integrated machine which comprises a hydraulic component, a rotor component of a motor, a stator component of the motor, a rotary drum and a shell component, wherein the hydraulic component comprises a flow distribution sliding disc pair, a flow distribution pair and a plunger pair, the rotary drum is respectively connected with a cylinder body and the rotor component of the motor, so that the rotary drum, the cylinder body and the rotor component of the motor 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 oil in an oil inlet of the shell component and/or a shell cavity enters a plunger hole of the cylinder body through the flow distribution pair or the flow distribution sliding disc pair. The electro-hydraulic integrated machine has the advantages of high electro-hydraulic fusion, compact structure, low noise, high efficiency, energy conservation, high power density, long service life and the like.

Description

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 compact electro-hydraulic integrated machine.

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. At present, most of hydraulic power units in a conventional hydraulic system using an electric motor as a prime mover are formed by connecting a plurality of dispersed independent components, as shown in fig. 1, a hydraulic transmission unit includes independent components such as a hydraulic pump 1, an electric motor 2, and a coupling 3, wherein the electric motor 2 provides mechanical energy to drive the hydraulic pump 1 to operate, so as to convert the mechanical energy of the hydraulic pump 1 into hydraulic energy, and the hydraulic energy output by the hydraulic pump 1 provides hydraulic energy for an execution 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, the 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 warships 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 a motor is incorporated.

(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 distributed power unit cannot be absolutely guaranteed, and mechanical vibration and noise are easy to generate 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 obvious.

(4) Heat dissipation is difficult. The energy dissipation exists in the operation process of the motor, and 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 larger noise and motor energy consumption are caused.

(5) External leakage is easy to occur. The seals at the pipeline connecting positions and the hydraulic pump extension position between the hydraulic pump and the oil tank lead the sealing device to be corroded and worn under the long-term working condition, thereby generating external leakage, 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.

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 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 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 rotor assembly of the motor, so that the rotating drum, the cylinder body and the rotor assembly of the motor 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 oil in an oil inlet of the shell assembly and/or a shell cavity enters a plunger hole of the cylinder body through the flow distribution pair or the flow distribution sliding disc pair.

According to the compact electro-hydraulic integrated machine, the end seat is arranged in the cavity of the shell assembly, two ends of the hydraulic assembly are respectively supported on the end seat and the rear end cover of the shell assembly, and the end seat is fixedly supported on the front end cover of the shell assembly or the end seat and the front end cover are of an integrated structure.

The compact type electro-hydraulic integrated machine is characterized in that the 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 the cylinder body, the swash plate is supported on the rear end cover, the end seat is provided with an oil inlet hole and an oil inlet groove opening to the cavity of the shell, 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 compact type electro-hydraulic integrated machine is characterized in that the flow distribution sliding disc pair is a bidirectional high-low pressure flow distribution sliding disc pair, a low-pressure flow distribution window and a high-pressure flow distribution window are arranged on the swash plate and are respectively communicated with an oil inlet and an oil outlet arranged on the rear end cover, an oil inlet on the rear end cover is provided with an oil way leading to the low-pressure flow distribution window on the swash plate and an oil way leading to the cavity of the shell through an oil inlet fork, when the compact type electro-hydraulic integrated machine works, low-pressure oil enters a plunger hole of a cylinder body through an oil inlet groove of the end seat and two ways of the low-pressure flow distribution port of the flow distribution disc 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 to realize the suction and discharge of hydraulic oil.

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

According to the compact electro-hydraulic integrated machine, the swash plate is supported on the end seat, the swash plate is provided with the low-pressure flow distribution window, the flow distribution plate is supported on the rear end cover, the end seat is provided with the oil inlet hole and the oil inlet groove which is opened to the cavity of the shell, and the oil inlet hole is respectively communicated with the oil inlet groove of the end seat and the low-pressure flow distribution window of the swash plate.

The compact electro-hydraulic integrated machine is characterized in that the flow distribution pair is a bidirectional high-low pressure flow distribution pair, a low-pressure flow distribution port and a high-pressure flow distribution port which are separated are arranged on the flow distribution plate and are respectively communicated with an oil inlet and an oil outlet of the rear end cover, an oil inlet on the rear end cover is provided with an oil way leading to the low-pressure flow distribution port on the flow distribution plate and an oil way leading to the cavity of the shell through an oil inlet fork, when the compact electro-hydraulic integrated machine works, low-pressure oil enters a plunger hole of a cylinder body from an oil inlet groove of the end seat through a low-pressure flow distribution window of the swash plate and a low-pressure flow distribution port of the flow distribution plate in a double-way manner, and high-pressure oil is discharged from a high-pressure flow distribution port of the flow distribution plate in a single-way manner, so that the suction and the discharge of the hydraulic oil are realized.

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

According to the compact electro-hydraulic all-in-one machine, the peripheral surface of the rotary drum is connected with a rotor assembly of a motor, a connecting part extending inwards is arranged on the inner side of the rotary drum, a plurality of oil passing holes are formed in the annular direction of the connecting part, the oil passing holes are communicated with the cavities of the shells on the two sides, so that low-pressure oil can smoothly pass through the oil passing holes, and a connecting key matched with the periphery of a cylinder body is arranged in the circumferential direction of the connecting part.

According to the compact electro-hydraulic integrated machine, the spring pre-tightening device is arranged between the sliding disc and the cylinder body, and the flow distribution sliding disc pair and the sliding disc pair have certain initial contact force through the spring pre-tightening device;

or, a restraining device is arranged on the sliding plate and/or the cylinder block, and the restraining device is used for limiting the sliding plate of the distribution sliding plate pair to move away from the swash plate and limiting the cylinder block of the distribution sliding plate pair to move away from the distribution plate.

According to the compact type electro-hydraulic integrated machine, the impeller is arranged in the end seat and on the main shaft, the end seat is provided with the plurality of communicating holes and the oil inlet hole communicated with the plunger hole of the cylinder body, and the impeller is driven by the main shaft to accelerate low-pressure oil in the cavity of the shell to enter the plunger hole through the communicating holes and take away heat through the oil inlet hole.

The compact type electro-hydraulic all-in-one machine is characterized in that the hydraulic assembly is of a shaft supporting type structure, the 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 compact electro-hydraulic integrated machine comprises a hydraulic assembly, a fourth bearing, a fifth bearing, a rotor assembly of a motor and the hydraulic assembly, wherein the hydraulic assembly is of a rotary drum supporting type structure, the fourth bearing and the fifth bearing are respectively clamped between the rotary drum and a shell assembly, the rotor assembly and the hydraulic assembly of the motor are supported on the shell assembly through the rotary drum, the fourth bearing and the fifth bearing and realize synchronous rotation, the 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, a coupler and the like 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 power density requirements such as engineering machinery, electric automobiles, robots, aerospace, ships and the like.

(2) 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.

(3) 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, the coupling, the air cooling device and the connecting pipeline are eliminated, the influence of the three on noise and vibration is fundamentally eliminated, and the noise is obviously reduced.

(4) The invention has self-cooling and easy heat dissipation. The electro-hydraulic integrated machine is highly integrated, low-pressure oil is led to an oil path double-path oil inlet in a cavity of a shell through an oil path of a low-pressure flow distribution window on a swash plate and an oil inlet fork, wherein the oil path oil inlet led to the cavity of the shell can take away heat generated by three friction pairs of a stator, a rotor and hydraulic pressure of the motor and enter a hydraulic system, and self-cooling is realized.

(5) 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 sliding disc 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 stability of an oil film of the friction pairs, and enables a 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 side oil inlet amount to be remarkably increased, so that the self-suction capacity and the self-suction rotating speed can be greatly improved, and the damage of cavitation to the three-large friction pair is reduced.

(6) 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.

(7) 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 of 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 cross-sectional view B-B of the slider structure 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 a bearing surface at one end of the port plate of the present invention.

Fig. 11 is a plan view of one end of the cylinder body in the present invention.

FIG. 12 is a cross-sectional view of the drum of the present invention taken along the axis thereof.

FIG. 13 is a plan view of one side of the drum of the present invention.

FIG. 14 is a cross-sectional view of the end block of the present invention taken along the axis.

FIG. 15 is a cross-sectional view taken along line C-C of FIG. 14 in accordance with the present invention.

FIG. 16 is another embodiment of the electrohydraulic all-in-one machine of the invention.

FIG. 17 is a bearing surface of one end of the port plate of the embodiment of FIG. 16 of the present invention.

FIG. 18 shows an embodiment of the electrohydraulic integrated machine for preloading the center spring in the invention.

Fig. 19 is an embodiment of the electrohydraulic all-in-one machine with the impeller device in the invention.

FIG. 20 shows an embodiment of the present invention in the form of a drum-supported electro-hydraulic machine.

FIG. 21 is a sectional view taken along line A-A of FIG. 20 according to 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 hanging 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, 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, 17 is a second stop, 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, 34 is a shell cavity, 35 end seat, 36 is a communicating hole, 37 is an oil inlet groove, 38 is an oil inlet hole, 39 supporting partition parts, 40 is a swash plate, 41 is a swash plate bearing surface, 41a is a bearing stop part, 42 is a flow distribution oil groove, 43 is a low-pressure flow distribution window, 44 is a high-pressure flow distribution window, 50 is a slide plate, 50C is a slide plate axis, 51 is a slide plate static pressure bearing surface, 52 is a slide plate boss surface, 53 is a slide plate kidney-shaped hole, 54 is a slide plate outer sealing part, 55 is a slide plate inner sealing part, 56 is a slide plate partition sealing part, 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 central hole, 73 is a tapered rod part, 74 is a plunger part, 80 is a cylinder body, 81 is a plunger hole, 82 is a main shaft assembling hole, 83 is a cylinder body static pressure bearing surface, 84 is an oil through hole, 85 is a cylinder body kidney-shaped hole, 90 is a flow distribution plate, 91 is a bearing surface, 92 is a low-pressure flow distribution port, 93 is a high-pressure flow distribution port, 100 is a center spring, 101 is a retainer ring, 102 is a ball hinge, 141 is a snap spring, and 150 is an impeller.

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, embodiments of the present invention are illustrated in a typical orientation such that when the central axis of the main shaft of the electro-hydraulic integrated machine is at a horizontal rest with the front end cover side to the left and the rear end cover to the right, 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 only for the purpose of facilitating the description of the invention and simplifying the description, and not to indicate or imply that the device or element being referred to must have a particular orientation, as well as a particular orientation configuration and operation, it being understood that the invention may be manufactured, stored, transported, used, and sold in an orientation other than the position described.

Example 1:

as shown in fig. 2 to 15, which are preferred embodiments of the electro-hydraulic integrated machine 5 of the present invention, in the shown preferred embodiments, the electro-hydraulic integrated machine 5 is a shaft support structure, the electro-hydraulic integrated machine 5 includes a hydraulic assembly, a rotor assembly 9 of the motor, a stator assembly 8 of the motor, a drum 11, a housing assembly, a main shaft 10, a first bearing 21, and a second bearing 22, the hydraulic assembly includes a flow distribution sliding plate pair, a flow distribution pair, and a plunger pair, the plunger pair includes a plunger hole wall of a cylinder 80 and a plunger 70, preferably, the plunger 70 is a conical structure with a central large hole as a 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, wherein 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. The main shaft axis 10C of the main shaft 10 coincides with the 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, so that the rotating cylinder 11, the cylinder body 80 and the motor rotor assembly 9 synchronously rotate, and the plunger 70 reciprocates in a plunger cavity of the cylinder body 80 to realize oil suction and discharge work.

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

Preferably, the motor is an induction motor, 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 an insulating varnish on a surface, an outer circumferential surface of the stator core 8a is fixedly connected with the housing 31, an 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 for generating 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 arranged on the housing 31.

Specifically, the rotor assembly 9 of the motor comprises a rotor core 9a, a rotor winding 9b and other components, wherein the rotor core 9a is also a component of a motor magnetic circuit and is formed by punching and laminating thin silicon steel sheets coated with insulating paint on the surface, the inner circumferential surface of the rotor core 9a is fixedly connected with a rotating drum 11, the two side surfaces of the rotor core 9a abut against a protruding part 15 of the rotating drum 11 through a first stop 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 for generating induced current, the rotor winding 9b comprises but is not limited to a rotor winding with a squirrel-cage structure and a winding structure, wherein the squirrel-cage structure is formed by inserting copper bars or aluminum bars as guide bars into the slots on the rotor core 9a, 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 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 waist-shaped holes 53 of the sliding disc 50 are arranged at one end of the sliding disc 50, a plurality of plunger ball sockets 58 are arranged at the other end surface of the sliding disc 50, the waist-shaped holes 53 of 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 on the rear end cover 33 is arranged on the swash plate 40.

Specifically, the plunger pair includes a plunger 70 and a cylinder hole wall, 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 the plunger ball socket 58 and the 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, a cylinder static pressure bearing surface 83 is provided on an end surface of the end portion of the cylinder 80 facing the flow distribution plate 90, 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 a low pressure distribution port 92 is provided on the flow distribution plate 90, as shown in fig. 10.

Specifically, the outer peripheral surface of the rotary drum 11 is connected with a rotor assembly 9 of the motor, a connecting portion 12 extending inwards is arranged inside the rotary drum 11, a plurality of oil passing holes 13 are annularly arranged on the connecting portion 12, the oil passing holes 13 are communicated with the housing 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 circumferentially arranged inside the connecting portion 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 means further includes a second stopper 17 disposed in the outer circumferential direction of the cylinder 80 for restraining the axial displacement of the drum 11, and the second stopper 17 is connected to the connecting portion 12 of the 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 a rotor assembly of the motor, a stator assembly 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, an oil inlet 33a and an oil outlet 33b are provided on the rear end cover 33, an oil inlet branch 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 sucked, 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 window 43 of the swash plate 40, and the other part of the oil flows into the housing cavity 34 through the oil inlet 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 in the part flows through the housing cavity 34, each friction pair arranged in the housing cavity 34, a rotor assembly and a stator assembly of the motor are immersed in the low-temperature oil liquid, and heat generated by the stator assembly, the rotor assembly and the hydraulic friction pair of the motor is taken away to enter a hydraulic system, specifically shown in an internal liquid flow diagram of 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 an oil inlet 33a and an oil outlet 33b of the rear end cover; the flow distribution pair is a one-way low-pressure flow distribution pair, the flow distribution pair comprises a flow distribution disc 90 and the end part of a cylinder body 80 supported on the flow distribution disc 90, the flow distribution disc 90 and the end surface of the cylinder body 80 form a static pressure oil film support in clearance fit and the static pressure oil film support and the cylinder body 80 keep sliding fit, and one side of the flow distribution disc 90 opposite to a low-pressure side plunger plug hole 81 is provided with a low-pressure flow distribution port 92, wherein 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 to the front end cover 33 by 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 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 fluid 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 groove 37 of the end seat 35 through the low-pressure fluid distribution port 92 of the fluid distribution plate 90 and the low-pressure fluid distribution window 43 of the swash plate 40 in a double-path manner, and high-pressure oil is discharged from the high-pressure fluid distribution window 44 of the swash plate 40 in a single-path manner, so that the suction and the 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 traditional hydraulic power unit, wherein a motor 1, a hydraulic pump 2, a coupling 3 and the like are independent components which are axially arranged, the axial length is long, and the occupied space is large, fig. 2 is an electro-hydraulic integrated machine in the invention, the axial length is reduced by more than 60%, the occupied space is reduced by more than 50%, a motor and the hydraulic pump are highly integrated into a whole, the integral power density is large, and 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 motor, the hydraulic pump and the air cooling device 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 opposite to 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 at 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 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 plunger ball socket 58.

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

Wherein, an effective static pressure oil film support is formed between the convex table surface 52 of the sliding disc and the supporting surface of the swash plate 40, the convex table surface 52 of the sliding disc is provided with a sealing part for sealing oil, the sealing part is arranged on the inner periphery and the outer periphery of the waist-shaped hole 53 of the sliding disc in a state of surrounding the waist-shaped hole 53 of the sliding disc, the sealing part comprises an inner sealing part 55 of the sliding disc, an outer sealing part 54 of the sliding disc and an interval sealing part 56 of the sliding disc, the inner sealing part 55 of the sliding disc is a region surrounded by the inner edge of the waist-shaped hole 53 of the sliding disc and the inner diameter R1 of the convex table surface 52 of the sliding disc, the outer sealing part 54 of the sliding disc is a region surrounded by the outer edge of the waist-shaped hole 53 of the sliding disc and the outer diameter R2 of the convex table surface 52 of the sliding disc, the interval sealing part 56 of the sliding disc is a convex table surface region between the adjacent waist-shaped holes 53 of the sliding disc, a certain reasonable clearance is always kept between the sealing part of the convex table surface 52 of the sliding disc and the bearing surface of the swash plate 40, so that 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 by 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 through holes 84 for communicating the plunger holes 81 and the cylinder waist-shaped holes 85 are provided on the cylinder end.

In operation, hydraulic pressure acts on the end of the cylinder body and is further transmitted to the port plate 90. typically, the axial force of the hydraulic pressure acting on the end of the cylinder body 80 is greater than the bearing force of the port plate 90 acting on the end of the cylinder body through an oil film reaction, so that the end of the cylinder body slides against the port plate 90 through a layer of oil film at all times.

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 in clearance fit with the cylinder plunger hole wall 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 plunger central hole 72 is a large-aperture through hole structure and is used as a channel for sucking and/or discharging oil liquid; 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 disc 50, and in general, the axial force of the plunger 70 acting on the disc 50 is greater than the sum of the supporting force of the swash plate 40 acting on the disc 50 through oil film reaction and the return force of the plunger 70, so that the disc 50 slides against the swash plate 40 through a layer of oil film at all times.

Considering that the initial sealing between the sliding plate and the swash plate is still needed 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. 18, 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 disc 50, and the other end of the pre-tightening spring force acts on the end part of the cylinder body 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 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 41a and including a snap-fit circumferential groove provided on the bearing stopper 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 also conceivable to provide an elastic washer (not shown) between the stop and the third bearing 23 or between the circlip and the third bearing 23, so that the restraint assembly, in addition to limiting the displacement of the slide plate away from the swash plate end, also has a certain initial pretension to maintain the preloaded state of the slide plate and the swash plate. Similarly, the restraining manner of the engaging device can also be realized by the interference fit of the third bearing 23 and the swash plate supporting stop portion 41a, and the engaging circumferential groove and the snap spring engaged with the engaging circumferential groove are arranged on the swash plate supporting stop portion 41a and adjacent to the third bearing 23 to play a further restraining role. On the cylinder side, the restraint means further comprises a circlip 141 for restraining the cylinder end from moving away from the thrust plate.

Example 2:

as shown in fig. 19, the structure is different from that of embodiment 1 in that the oil inlet passage is different, and the flow distribution manner is different therefrom, and otherwise, the structure described with reference to embodiment 1 can be used.

Specifically, the flow distribution sliding disc pair is a one-way high-pressure flow distribution sliding disc pair, an oil inlet 33a on the rear end cover 33 is communicated with the housing cavity 34, low-pressure oil completely enters the housing cavity 34 from an oil inlet 33a of the rear end cover 33, a swash plate 40 in the flow distribution sliding disc pair is supported on the rear end cover 33, 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 arranged on the rear end cover 33, when the hydraulic pump works, the low-pressure oil in the housing cavity 34 enters a plunger hole 81 of the cylinder body 80 through a single way from an oil inlet groove 37 of the end seat 35 through a low-pressure flow distribution port 92 of the flow distribution disc 90, and the high-pressure oil is discharged through a single way from the high-pressure flow distribution window 44 of the swash plate 40, so that the hydraulic oil is sucked and discharged.

Example 3:

as shown in fig. 16, the difference from embodiment 1 is that the portions of the slide plate pair and the flow distribution pair which are opposed and abutted against each other are different, and the flow distribution passage is different therefrom, and the structure described in embodiment 1 can be referred to.

Specifically, the flow distribution sliding disc pair comprises a sliding disc 50 and a swash plate 40 supported on an end seat 35, the swash plate 40 and the end surface of the sliding disc 50 form a static pressure oil film support in clearance fit and are in sliding fit, the swash plate 40 is provided with a low-pressure flow distribution window 43, the end seat 35 is provided with an oil inlet groove 37 opening to the shell cavity 34 and an oil inlet hole 38, and the oil inlet hole 38 is communicated with the oil inlet groove 37 of the end seat 35 and the low-pressure flow distribution window 43 of the swash plate 40.

Wherein, the distribution pair comprises a cylinder end and a distribution plate 90 supported on the rear end cover 33, the cylinder end and the distribution plate support surface 91 form a static pressure oil film support in clearance fit, the distribution plate 90 is provided with a low pressure distribution port 92 and a high pressure distribution port 93 which are separated, the low pressure distribution port 92 and the high pressure distribution port 93 are respectively communicated with an oil inlet 33a and an oil outlet 33b of the rear end cover 33, the oil inlet 33a on the rear end cover 33 is provided with an oil path which leads to the low pressure distribution port 92 on the distribution plate 90 and an oil path which leads to the shell cavity 34 through a branch port 33c, when in operation, low pressure oil enters the plunger hole 81 of the cylinder 80 through two paths of the low pressure distribution window 43 of the swash plate 40 and the low pressure distribution port 92 of the distribution plate 90 from the oil inlet groove 37 of the end seat 35, and high pressure oil is discharged from the high pressure distribution port 93 of the distribution plate 90 in one path, the suction and the discharge of the hydraulic oil are realized.

Meanwhile, in order to stabilize the structure of the drum 11 during operation, a fourth bearing 24 is provided between the drum 11 and the end seat 35, a fifth bearing 25 is provided between the drum 11 and the rear end cover 33, and the drum 11 is supported by the fourth bearing 24 and the fifth bearing 25 to be rotatable about its own center.

Example 4:

the difference from the embodiments 1 and 2 lies in that the parts opposite and abutted to the flow distribution slide plate pair and the flow distribution pair and the oil inlet and oil passage of the rear end cover are different, and the structure of the flow distribution flow passage caused by the difference is otherwise as described with reference to embodiment 2.

Specifically, the flow distribution sliding disc pair comprises a sliding disc 50 and a swash plate 40 supported on an end seat 35, the swash plate 40 and the end surface of the sliding disc 50 form a static pressure oil film support in clearance fit and are in sliding fit, the swash plate 40 is provided with a low-pressure flow distribution window 43, the end seat 35 is provided with an oil inlet groove 37 and an oil inlet hole 38 which are opened to the shell cavity 34, and the oil inlet hole 38 is communicated with the oil inlet groove 37 of the end seat 35 and the low-pressure flow distribution window 43 of the swash plate 40.

The flow distribution pair is a one-way high-pressure flow distribution pair, a high-pressure flow distribution port 93 is arranged on the flow distribution plate 90, the high-pressure flow distribution port 93 is communicated with an oil outlet 33b arranged on the rear end cover 33, an oil inlet 33a on the rear end cover 33 is communicated with the housing cavity 34, low-pressure oil completely enters the housing cavity 34 from the oil inlet 33a on the rear end cover 33, during operation, the low-pressure oil in the housing cavity 34 enters the plunger hole 81 of the cylinder body 80 through the oil inlet groove 37 of the end seat 35 and the low-pressure flow distribution window 43 of the swash plate 40 in a one-way manner, and the high-pressure oil is discharged from the high-pressure flow distribution port 93 of the flow distribution plate 90 in a one-way manner, so that the suction and the discharge of the hydraulic oil are realized.

Example 5:

as shown in fig. 19, 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 distribution port 92 of the distribution 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 accelerates the low-pressure oil in the housing cavity 34 through the communication holes 36, enters the plunger hole 81 through the oil inlet hole 38, and takes away heat under the driving of the main shaft 10.

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. 20 and 21, the main difference from the other embodiments is that the embodiment is a drum-supported electro-hydraulic integrated 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 sandwiched between the drum 11 and the front end cap 32 or the rear end cap 33, respectively, or the fourth bearing 24 may be sandwiched between the drum 11 and the end seat 35. The rotor assembly 9 and the hydraulic assembly of the motor are supported on the shell assembly 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 which characterized in that: comprises a hydraulic component, a rotor component (9) of a motor, a stator component (8) of the motor, a rotating drum (11) and a shell component, 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 a rotor component (9) of the motor, so that the rotating drum (11), the cylinder body (80) and the rotor component (9) of the motor rotate synchronously, 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), and oil in an oil inlet of a shell component and/or a shell cavity (34) enters a plunger hole (81) of a cylinder body (80) through a flow distribution pair or a flow distribution sliding disc pair.

2. The compact electro-hydraulic integrated machine of claim 1, wherein: an end seat (35) is arranged in a shell cavity (34) of the shell assembly, two ends of the hydraulic assembly are respectively supported on the end seat (35) and a rear end cover (33) of the shell assembly, the end seat (35) is fixedly supported on a front end cover (32) of the shell assembly, or the end seat (35) and the front end cover (32) are of an integrated structure.

3. The compact electro-hydraulic integrated machine of claim 2, wherein: the flow distribution plate (90) is supported on an end seat (35), the flow distribution plate (90) is provided with a low-pressure flow distribution port (92) communicated with a plunger hole (81) of a cylinder body (80), the swash plate (40) is supported on a rear end cover (33), the end seat (35) is provided with an oil inlet hole (38) and an oil inlet groove (37) opened to a 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 flow distribution port (92) of the flow distribution plate (90).

4. The compact electro-hydraulic integrated machine of claim 3, wherein: the flow distribution sliding disc pair is a bidirectional high-low pressure flow distribution sliding disc pair, 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) arranged on the rear end cover (33), an oil inlet (33a) on the rear end cover (33) is provided with an oil path which leads to the low-pressure flow distribution window (43) on the swash plate (40) and an oil path 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 the cylinder body (80) through a low-pressure flow distribution port (92) of the flow distribution disc (90) and a low-pressure flow distribution window (43) of the swash plate (40) in a double-path manner from an oil inlet groove (37) of the end seat (35), and the high-pressure oil is discharged from the high-pressure flow distribution window (44) of the swash plate (40) in a single path, the suction and the discharge of the hydraulic oil are realized.

5. The compact electro-hydraulic integrated machine of claim 3, wherein: the flow distribution sliding disc pair is a one-way high-pressure flow distribution sliding disc pair, 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) arranged on the rear end cover (33), an oil inlet (33a) on the rear end cover (33) is communicated with the shell cavity (34), all low-pressure oil enters the shell cavity (34) from the oil inlet (33a) on the rear end cover (33), when the hydraulic pump 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 disc (90) from an oil inlet groove (37) of the end seat (35) in a one way, 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 suction and the discharge of the hydraulic oil are realized.

6. The compact electro-hydraulic integrated machine of claim 2, wherein: the swash plate (40) is supported on an end seat (35), a low-pressure flow distribution window (43) is arranged on the swash plate (40), the flow distribution plate (90) is supported on a rear end cover (33), an oil inlet hole (38) and an oil inlet groove (37) which is opened to a shell cavity (34) are arranged on the end seat (35), 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 window (43) of the swash plate (40).

7. The compact electro-hydraulic integrated machine of claim 6, wherein: the flow distribution pair is a bidirectional high-low pressure flow distribution pair, a low-pressure flow distribution port (92) and a high-pressure flow distribution port (93) which are separated are arranged on the flow distribution plate (90), the low-pressure flow distribution port (92) and the high-pressure flow distribution port (93) are respectively communicated with an oil inlet (33a) and an oil outlet (33b) of a rear end cover (33), an oil inlet (33a) on the rear end cover (33) is provided with an oil path which leads to the low-pressure flow distribution port (92) on the flow distribution plate (90) and an oil path which leads to the shell cavity (34) through an oil inlet fork (33c), when the flow distribution pair works, low-pressure oil enters a plunger hole (81) of a cylinder body (80) through two paths from an oil inlet groove (37) of the end seat (35) through a low-pressure flow distribution window (43) of a swash plate (40) and the low-pressure flow distribution port (92) of the flow distribution plate (90), and the high-pressure oil is discharged from the high-pressure flow distribution port (93) of the flow distribution plate (90) in a single path, the suction and the discharge of the hydraulic oil are realized.

8. The compact electro-hydraulic integrated machine of claim 6, wherein: the hydraulic oil distribution pair is a one-way high-pressure distribution pair, a high-pressure distribution port (93) is arranged on the distribution plate (90), the high-pressure distribution port (93) is communicated with an oil outlet (33b) arranged on the rear end cover (33), an oil inlet (33a) on the rear end cover (33) is communicated with the shell cavity (34), all low-pressure oil enters the shell cavity (34) from the oil inlet (33a) on the rear end cover (33), when the hydraulic oil distribution pair works, the low-pressure oil in the shell cavity (34) enters a plunger hole (81) of a cylinder body (80) through a low-pressure distribution window (43) of a swash plate (40) from an oil inlet groove (37) of an end seat (35) in a one-way mode, and the high-pressure oil is discharged from the high-pressure distribution port (93) of the distribution plate (90) in a one-way mode, so that the suction and the discharge of the hydraulic oil are realized.

9. The compact electro-hydraulic integrated machine of claim 1, wherein: the outer peripheral surface of the rotary drum (11) is connected with a rotor assembly (9) of the motor, a connecting portion (12) extending inwards is arranged on the inner side of the rotary drum (11), a plurality of oil passing holes (13) are formed in the annular direction of the connecting portion (12), the oil passing holes (13) are communicated with shell cavities (34) on two sides to enable low-pressure oil to pass through smoothly, and connecting keys (14) matched with the outer peripheral direction of the cylinder body (80) are arranged in the inner peripheral direction of the connecting portion (12).

10. The compact electro-hydraulic integrated machine of claim 1, wherein: a spring pre-tightening device is arranged between the sliding disc (50) and the cylinder body (80), and a certain initial contact force is formed between the flow distribution sliding disc pair and the sliding disc pair through the spring pre-tightening device;

or, a restraining device is arranged on the sliding plate (50) and/or the cylinder body (80), and the restraining device limits the movement of the sliding plate (50) of the distribution sliding plate pair away from the swash plate (40) and limits the movement of the cylinder body (80) of the distribution sliding plate pair away from the distribution plate (90).

11. The compact electro-hydraulic integrated machine of claim 2, wherein: an impeller (150) is arranged in the end seat (35) and on the main shaft (10), a plurality of communicating holes (36) and oil inlet holes (38) communicated with the plunger holes (81) of the cylinder body (80) 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 holes (81) through the communicating holes (36) and take away heat through the oil inlet holes (38).

12. The compact electro-hydraulic integrated machine of any one of claims 1-11, wherein: 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.

13. The compact electro-hydraulic integrated machine of any one of claims 1-11, wherein: 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) of the motor 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.