CN116771739A

CN116771739A - Electric hydraulic cylinder

Info

Publication number: CN116771739A
Application number: CN202310863820.2A
Authority: CN
Inventors: 张海铎; 丁连生; 蒋涛; 张迎新; 毛锋; 张玉波; 赵灵毓; 李丹; 李继宝; 刘雪松; 王璐; 姚胜
Original assignee: Changchun Yidong Automobile Parts Manufacturing Co ltd
Current assignee: Changchun Yidong Automobile Parts Manufacturing Co ltd
Priority date: 2023-07-14
Filing date: 2023-07-14
Publication date: 2023-09-19

Abstract

An electrohydraulic cylinder belongs to the technical field of automobile parts. The invention aims to integrate an electric pump, a manual pump, an oil pipe and a hydraulic cylinder together, thereby not only supplying oil, but also realizing the function of a hydraulic lifting system. The motor is arranged on the side surface of the cylinder body of the hydraulic cylinder, a buffer blocking piece is arranged between the motor and the side surface of the cylinder body, the side surface of the pump body is fixedly connected with the side surface of the U-shaped clamp at the lower end of the hydraulic cylinder, and a sealed self-oil supply tank is arranged between the motor and the pump body; the upper half part of the pump body is an oil self-supply mechanism, and the lower half part of the pump body is a pump body oil way; the pump body and the pump body protruding ring are integrated into a whole to form the whole pump body. The invention opens the power generation hydraulic cylinder, which is equivalent to integrating the electric pump, the manual pump, the oil cylinder, the hydraulic cylinder and the like, and has the advantages of integration, less parts, low management cost, simple assembly, high efficiency, small occupied space, convenient whole vehicle arrangement, light weight and the like.

Description

Electric hydraulic cylinder

Technical Field

The invention belongs to the technical field of automobile parts.

Background

The hydraulic cylinder is a hydraulic actuating element which converts hydraulic energy into mechanical energy and performs linear reciprocating motion (or swinging motion), has simple structure and reliable work, and can dispense with a speed reducing device when being used for realizing reciprocating motion, thus being applied to a plurality of industries. The common hydraulic lifting system in the current market comprises an electric pump, a manual pump, an oil pipe and a hydraulic cylinder, is independently developed and independently supplied, and is installed in a whole vehicle factory, so that the defects of multiple parts, high management cost, complex assembly, low efficiency, large occupied space, inconvenience in whole vehicle arrangement, heavier whole weight and the like exist.

Disclosure of Invention

The invention aims to integrate an electric pump, a manual pump, an oil pipe and a hydraulic cylinder together, thereby not only supplying oil, but also realizing the function of a hydraulic lifting system.

The motor is arranged on the side surface of the cylinder body of the hydraulic cylinder, a buffer blocking piece is arranged between the motor and the side surface of the cylinder body, the side surface of the pump body is fixedly connected with the side surface of the U-shaped clamp at the lower end of the hydraulic cylinder, and a sealed self-oil supply tank is arranged between the motor and the pump body; the upper half part of the pump body is an oil self-supply mechanism, and the lower half part of the pump body is a pump body oil way; the pump body and the pump body protruding ring are integrated into a whole to form the whole pump body;

the shaft of the motor in the self-oil supply tank is fixedly connected with the top end of the long connecting shaft, and the lower end of the long connecting shaft is fixedly inserted into an inserting hole at the top end of the eccentric cylinder body; the inside of the self-supply oil tank is provided with a self-supply oil cavity;

self-oil supply mechanism: an oil supply groove is formed in the upper half part of the pump body, and an oil distributing shaft mounting hole is formed in the center of the lower half part of the pump body; the side wall of the oil supply groove is provided with a ring groove; the eccentric cylinder body is placed in the oil supply groove, the eccentric cylinder body and the oil supply groove are in an eccentric state, the lower surface of the bearing outer tile is clamped on the lower edge of the annular groove, the upper surface of the bearing outer tile is tightly pressed by the limiting check ring, and the upper end of the limiting check ring is clamped on the upper edge of the annular groove;

the upper end of the oil distributing shaft is inserted into an insertion hole at the lower end of the eccentric cylinder body in a micro clearance fit manner, the lower end of the oil distributing shaft is inserted into an oil distributing shaft mounting hole in an interference fit manner, two semicircular hole grooves with lateral openings are formed at the upper end of the oil distributing shaft, a negative pressure piston pin hole is formed in the eccentric cylinder body corresponding to the axial positions of the semicircular hole grooves, a piston pin is placed in the negative pressure piston pin hole, two longitudinal oil passages, namely a left longitudinal oil passage and a right longitudinal oil passage, are formed in the oil distributing shaft, the upper ends of the two longitudinal oil passages are respectively communicated with the two semicircular hole grooves, and the lower ends of the two longitudinal oil passages are respectively communicated with the left oil distributing passage and the right oil distributing passage in the oil pump body;

pump body oil circuit: an oil suction passage is longitudinally formed in the pump body, the middle part of the oil suction passage is communicated with a first transverse oil passage, the first transverse oil passage is communicated with a reversing valve cavity, two ends of the reversing valve cavity are respectively communicated with a right oil cavity of the reversing valve and a left oil cavity of the reversing valve, the middle part of the reversing valve is arranged in the reversing valve cavity, a reversing valve spring is sleeved on a reversing valve middle rod, and two ends of the reversing valve spring are respectively propped against the bottoms of reversing valve blocking heads at two ends of the reversing valve middle rod;

the oil cavity on the right side of the reversing valve is communicated with the oil distribution channel on the left side through a first branch oil way, the oil distribution channel on the left side is communicated with the back cavity of the reversing valve body through a second branch oil way, the reversing valve body is arranged in the back cavity of the reversing valve body, the back end of the reversing valve body is propped against the blocking of the back cavity of the reversing valve body, the front end of the reversing valve body is blocked at the joint of the front cavity of the reversing valve body and the back cavity of the reversing valve body, the reversing valve body is sealed outside the reversing valve body through an O-shaped sealing ring, a reversing valve body through hole is transversely formed in the reversing valve body, the back cavity of the reversing valve body is communicated with the inner cavity of the reversing valve body, the front end of the inner cavity of the reversing valve body is communicated with the front cavity of the reversing valve body, a guide spring is arranged in the front cavity of the reversing valve body, the bottom end of the guide spring is propped against the front end wall of the front cavity of the reversing valve body, the ball seal is arranged in the guide spring, and the ball seal diameter is larger than the pipe diameters of the connecting channel and the inner cavity of the reversing valve body;

the left oil cavity of the reversing valve is communicated with the right oil distribution passage through a third branch oil passage, the right oil distribution passage is communicated with the throttle valve rear cavity through a fourth branch oil passage, a throttle valve is arranged in the throttle valve cavity, an O-shaped sealing ring is sleeved outside the throttle valve, the throttle valve cavity is divided into a throttle valve front cavity and a throttle valve rear cavity, the front end of the throttle valve is conical and corresponds to a throttle passage, and a through throttle valve inner passage is formed in the throttle valve;

the oil cavity at the left side of the reversing valve is communicated with a bent pipe passage in the bent pipe joint through a fifth branch oil passage, and the bent pipe passage is communicated with the hydraulic lock;

the throttle channel is communicated with a lower oil injection passage in the U-shaped clamp through a sixth branch oil passage, and a lower oil injection nozzle is arranged between the sixth branch oil passage and the lower oil injection passage;

the front cavity of the reversing valve body is communicated with an eighth branch oil way through a seventh branch oil way, the eighth branch oil way is communicated with an upper oil injection passage in the U-shaped clamp through a ninth branch oil way, and an upper oil injection nozzle is arranged between the ninth branch oil way and the upper oil injection passage; the eighth branch oil way is communicated with the overflow mechanism through a tenth branch oil way, and the overflow mechanism is provided with: the tenth branch oil way is communicated with the overflow branch oil way, the overflow branch oil way is communicated with the overflow valve cavity, an overflow valve spring is arranged in the overflow valve cavity, the front end of the overflow valve spring is propped against an overflow ball valve, the overflow ball valve is arranged between the overflow valve cavity and the overflow branch oil way, the diameter of the overflow ball valve is larger than that of the overflow branch oil way, a pressure regulating push rod is inserted at the rear end of the overflow valve spring, the rear end of the pressure regulating push rod is propped against a pressure regulating nut, and the pressure regulating nut is fixed in the overflow valve cavity; the overflow valve cavity enters the oil suction passage through the oil suction passage oil inlet;

the throttle valve front cavity is communicated with a return oil way through an eleventh branch oil way, and an oil return port throttle valve is arranged at an oil outlet of the return oil way and is communicated with the self-supply oil cavity.

The invention is characterized in that a guide cover is sleeved outside a long connecting shaft, the upper part of the guide cover is a conical guide sleeve, the lower part of the guide cover is a guide cover, and the outer edge of the lower end of the guide cover is clamped on a limiting retainer ring in a ring groove.

The invention opens the power generation hydraulic cylinder, which is equivalent to integrating the electric pump, the manual pump, the oil cylinder, the hydraulic cylinder and the like, and has the advantages of integration, less parts, low management cost, simple assembly, high efficiency, small occupied space, convenient whole vehicle arrangement, light weight and the like.

Drawings

FIG. 1 is a schematic diagram of the structure of a hydraulic cylinder side-mounted whole hydraulic tank mechanism of the present invention;

FIG. 2 is a schematic view of the hydraulic cylinder of the present invention with the entire hydraulic tank mechanism mounted laterally and with the tank housing removed;

FIG. 3 is a schematic view of the exterior construction of a pump body portion of the present invention;

FIG. 4 is a top plan view of the exterior of the pump body of the present invention;

FIG. 5 is an exterior side view of the pump body of the present invention;

FIG. 6 is a B-B cross-sectional view of FIG. 5 in accordance with the present invention;

FIG. 7 is a cross-sectional view of F-F of FIG. 4 in accordance with the present invention;

FIG. 8 is a cross-sectional view A-A of FIG. 5 in accordance with the present invention;

FIG. 9 is a cross-sectional view of the C-C of FIG. 4 in accordance with the present invention;

FIG. 10 is a sectional view of the G-G of FIG. 4 according to the present invention;

FIG. 11 is a J-J cross-sectional view of FIG. 10 in accordance with the present invention;

FIG. 12 is a cross-sectional H-H view of FIG. 4 in accordance with the present invention;

FIG. 13 is a top view of the exterior of the pump body of the present invention with all negative pressure sump internals removed;

FIG. 14 is a middle side cross-sectional view of FIG. 13 of the present invention;

FIG. 15 is a side cross-sectional view of the eccentric cylinder of the present invention;

FIG. 16 is a schematic view of the pod assembly of the present invention.

Detailed Description

The self-oil supply structure of the invention is divided into three parts: the power input part, the oil tank part and the pump body oil circuit part. The power input part drives the self-oil supply mechanism to operate through the operation of the motor 3, so that hydraulic oil in the oil tank and the hydraulic cylinder are circulated through the pump body oil way part.

The motor 3 of the present invention is arranged on the side of the hydraulic cylinder body 1, and a buffer blocking member 2 is arranged between the motor 3 and the hydraulic cylinder body 1, and the buffer blocking member 2 can be arranged on the motor 3 or the hydraulic cylinder body 1, and the motor is made of a relatively soft material, for example: since the motor 3 is relatively close to the cylinder block 1, the rubber is blocked by the buffer stopper 2 to prevent collision. The side surface of the pump body 5 is fixedly connected with the side surface of a U-shaped clamp 6 at the lower end of the hydraulic cylinder, and a sealed self-oil supply tank 4 is arranged between the motor 3 and the pump body 5; the motor 3, the self-oil supply tank 4 and the pump body 5 form an improved part of the invention, the motor 3 adopts the existing motor, the invention is not repeated, and the invention mainly improves an oil supply part and an oil supply path part which are formed by taking the motor 3 as input power.

The upper half part of the pump body 5 is a self-oil supply mechanism, and the lower half part is a pump body oil way. The self-oil supply mechanism is a set of mechanical working part, and the oil tank and the hydraulic oil in the oil way of the pump body are circulated through the cooperation of all parts. The pump body oil way is a communication oil way for communicating the oil tank with the inside of the hydraulic cylinder.

The pump body 5 and the pump body protruding ring 12 are integrated to form the whole pump body; the pump body projecting ring 12 is an auxiliary portion that projects from the upper surface of the pump body 5. Because the upper surface of the pump body 5 is fixedly sealed with the bottom of the oil tank shell of the self-powered oil tank 4, the pump body protruding ring 12 is additionally arranged, so that the installation of the oil tank shell is convenient (only the bottom of the oil tank shell is required to be surrounded outside the pump body protruding ring 12), and the sealing is convenient (the sealing is particularly critical because the pressure in the oil tank is changed frequently).

The shaft of the motor 3 in the self-oil supply tank 4 is fixedly connected with the top end of the long connecting shaft 8, and the lower end of the long connecting shaft 8 is fixedly inserted into an inserting hole 23 at the top end of the eccentric cylinder body 9; the inside of the self-oil supply tank 4 is provided with a self-oil supply cavity 7; this part is the mechanical connection part where the motor shaft transmits power to the eccentric cylinder 9 and is placed in the self-oil chamber 7, and when the motor 3 rotates, it will rotate simultaneously with the eccentric cylinder 9 by the long connecting shaft 8. The eccentric cylinder 9 is inserted into the insertion hole 23 and can be fixed in various ways, such as a pin, a bolt, etc.

The upper half self-oil supply mechanism and the lower half pump oil passage in the pump body 5 will be described in detail below:

self-oil supply mechanism: the upper half part of the pump body is provided with an oil supply groove 14, and the center of the lower half part of the pump body is provided with an oil dividing shaft mounting hole 27; the side wall of the oil supply tank 14 is provided with a ring groove 76; this part is in the form of a slot in the upper half of the pump body 5, from the oil supply, see in particular fig. 14. The ring groove 76 is an annular inner groove opened on the inner wall of the pump body 5.

The eccentric cylinder 9 is placed in the oil feed groove 14, and the eccentric cylinder 9 is eccentric to the oil feed groove 14, that is, the axis of the eccentric cylinder 9 is parallel to but not the same as the axis of the oil feed groove 14, so that the axis of the eccentric cylinder 9 always rotates around the axis of the oil feed groove 14.

The lower surface of the outer tile of the bearing 13 is clamped on the lower edge 74 of the ring groove 76, the upper surface of the outer tile of the bearing 13 is tightly pressed by the limiting retainer ring 15, and the upper end of the limiting retainer ring 15 is clamped on the upper edge 75 of the ring groove 76; the stop collar 15 is an incompletely closed annular structure. When the bearing 13 is installed, the bearing outer tile is placed in the annular groove 76, the bearing outer tile is placed on the lower edge 74, then the limiting retainer ring 15 is compressed, the outer diameter of the limiting retainer ring 15 is smaller than the inner diameter of the upper end of the oil supply groove 14, after the bearing outer tile is placed in the annular groove 76, the compression state is released, the limiting retainer ring 15 is expanded and tightly pressed on the bearing outer tile, the upper end of the limiting retainer ring is attached to the upper edge 75, and accordingly the bearing 13 outer tile is fastened in the lower annular groove 76.

The upper end of the oil distributing shaft 22 is inserted into the jack at the lower end of the eccentric cylinder body 9 in a micro clearance fit manner, and the lower end of the oil distributing shaft 23 is inserted into the oil distributing shaft mounting hole 27 in an interference fit manner. This section is a description of the connection/communication of the two ends of the oil separating shaft 22 with the oil supply mechanism and the oil passage of the pump body, respectively. The micro clearance fit means that the gap between the outer wall of the oil distributing shaft 22 and the jack at the lower end of the eccentric cylinder body 9 is extremely tiny, so that the oil distributing shaft 22 is not driven when the eccentric cylinder body 9 rotates, and the hydraulic oil at the upper end can flow through the gap, and the micro clearance is similar to the micro clearance between the outer wall of the piston and the inner wall of the piston cylinder when the piston moves up and down in the piston cylinder. The interference fit means that the lower end of the oil distribution shaft 23 is substantially fixed after being inserted into the oil distribution shaft mounting hole 27.

Two semicircular hole grooves 17 with lateral openings are formed in the upper end of the oil distributing shaft 22, the structure of the semicircular hole grooves 17 is shown in a top view mode in fig. 6 and a test mode in fig. 9, a negative pressure piston pin hole 18 is formed in the eccentric cylinder body 9 corresponding to the axial position of the semicircular hole grooves 17, that is, the two semicircular hole grooves 17 are communicated with the negative pressure piston pin hole 18, a piston pin 19 is placed in the negative pressure piston pin hole 18, and the piston pin 19 is placed in the negative pressure piston pin hole 18 like a piston and can move in the negative pressure piston pin hole 18. The number of the negative pressure piston pin holes 18 depends on the actual use, and five holes are formed in the present invention, and a piston pin 19 is disposed in each negative pressure piston pin hole 18 (see fig. 6).

Referring to fig. 15, for convenience of explanation, the eccentric cylinder 9 is divided into three areas, an upper area is an area a, a middle area is an area B, a lower area is an area C, the area C is disposed below the bearing 13, and an upper surface D of the area C corresponds to a bottom surface of the bearing inner shoe but leaves a gap, the negative pressure piston pin hole 18 is a through hole, and the position B is disposed, since an axis of the eccentric cylinder 9 is offset from an axis of the bearing 13 (an axis of the bearing 13 is the same as an axis of the oil supply groove 14), one side of the eccentric cylinder 9 is in contact with the inner shoe of the bearing 13, and the other side of the eccentric cylinder 9 is out of contact with the bearing 13, and a larger gap is generated, but the gap must be smaller than a length of the piston pin 19 in the negative pressure piston pin hole 18, so that the piston pin 19 is prevented from being separated.

Two longitudinal oil passages, namely a left longitudinal oil passage 20 and a right longitudinal oil passage 21, are formed in the oil distributing shaft 22, the upper ends of the two longitudinal oil passages are respectively communicated with the two semicircular hole grooves 17, and the lower ends of the two longitudinal oil passages are respectively communicated with a left oil distributing passage 32 and a right oil distributing passage 50 in the oil way of the pump body; this portion is an oil path portion where the rear side of the piston pin 19 of the negative pressure piston pin hole 18 communicates with the pump body oil path, that is, the hydraulic oil of the pump body oil path can be sucked or squeezed out of the negative pressure piston pin hole 18 through the left side oil distribution passage 32 and the right side oil distribution passage 50, the left side longitudinal oil distribution passage 20, and the right side longitudinal oil distribution passage 21, respectively, in which the lower hydraulic oil is sucked into the negative pressure piston pin hole 18 when the piston pin 19 moves to the outside of the negative pressure piston pin hole 18, and the hydraulic oil sucked into the negative pressure piston pin hole 18 is squeezed out when the piston pin 19 moves to the inside of the negative pressure piston pin hole 18, thereby reciprocating.

When the eccentric cylinder 9 rotates, the piston pin 19 in the negative pressure piston pin hole 18 far from the bearing 13 is thrown to one end outside the negative pressure piston pin hole 18, so that negative pressure is formed at the rear side of the piston pin 19 in the negative pressure piston pin hole 18, at the moment, the lower hydraulic oil is sucked in, and the piston pin 19 in the negative pressure piston pin hole 18 near to the bearing 13 is extruded into the negative pressure piston pin hole 18, so that the hydraulic oil at the rear side of the piston pin 19 is extruded out.

Pump body oil circuit: an oil suction passage 10 is longitudinally formed in the pump body 5, the middle part of the oil suction passage 10 is communicated with a first transverse oil passage 25 (see fig. 7), the first transverse oil passage 25 is communicated with a reversing valve cavity 28, two ends of the reversing valve cavity 28 are respectively communicated with a reversing valve right-side oil cavity 31 and a reversing valve left-side oil cavity 53, the middle part of the reversing valve 24 is arranged in the reversing valve cavity 28, a reversing valve spring 29 is sleeved on a middle rod of the reversing valve 24, and two ends of the reversing valve spring 29 are respectively propped against the bottoms of reversing valve plugs 30 at two ends of a middle rod of the reversing valve 24 (see fig. 8; the rod of the reversing valve 24 is arranged in the reversing valve cavity 28, the length of the rod of the reversing valve 24 is larger than that of the reversing valve cavity 28, reversing valve plugs 30 are arranged at two ends of the rod of the reversing valve 24, the diameter of each reversing valve plug 30 is larger than the cavity inner diameter of the reversing valve cavity 28, and under the action of pressure, no matter which end of the reversing valve 24 moves, the reversing valve plugs 30 can finally plug one side of the reversing valve cavity 28, and the other side of the reversing valve cavity is communicated, namely one end of each reversing valve plug is plugged and the other end of each reversing valve cavity is open. The movement of the reversing valve 24 is determined by oil pressure, the end with high pressure is blocked, and the end with low pressure is unobstructed. The reversing valve spring 29 plays a guiding role, and when the reversing valve reverses, the reversing valve spring 29 moves along the axis direction of the pump body matching hole, and meanwhile, the gap of the spring link forms an oil groove for hydraulic oil to pass through.

The right oil cavity 31 of the reversing valve is communicated with the left oil distribution channel 32 through a first branch oil channel 52, the left oil distribution channel 32 is communicated with the reversing valve body rear cavity 37 through a second branch oil channel 33, the reversing valve body 36 is placed in the reversing valve body rear cavity 37, the rear end of the reversing valve body 36 is propped against the reversing valve body cavity plug 35, the front end of the reversing valve body 36 is clamped at the joint of the reversing valve body front cavity 47 and the reversing valve body rear cavity 37, the reversing valve body 36 is sealed by an O-shaped sealing ring, the reversing valve body 36 is transversely provided with a reversing valve body through hole 34, the reversing valve body through hole 34 is communicated with the reversing valve body rear cavity 37 and the reversing valve body cavity 38, the front end of the reversing valve body cavity 38 is communicated with the reversing valve body front cavity 47, a guide spring 39 is arranged in the reversing valve body front cavity 47, the bottom end of the guide spring 39 is propped against the front end wall of the reversing valve body 36, the ball seal 41 is placed in the guide spring 39, and the diameter of the ball seal 41 is larger than the diameters of the connecting channel 43 and the reversing valve body cavity 38; in this part, see the upper part of fig. 8, the ball seal 41 is forced to roll in the guide spring 39, when rolling between the connecting channel 43 and the reversing valve body front cavity 47, the passage between the connecting channel 43 and the reversing valve body front cavity 47 is blocked, and when rolling to the front ends of the reversing valve body front cavity 47 and the reversing valve body inner cavity 38, the passage between the reversing valve body front cavity 47 and the reversing valve body inner cavity 38 is blocked. The O-ring seal prevents hydraulic oil in the reversing valve body rear chamber 37 from directly entering the reversing valve body front chamber 47, which must communicate with the reversing valve body front chamber 47 through the reversing valve body inner chamber 38.

The left oil cavity 53 of the reversing valve is communicated with the right oil distribution passage 50 through a third branch oil passage 51, the right oil distribution passage 50 is communicated with the throttle back cavity 48 through a fourth branch oil passage 49, a throttle valve 45 is arranged in the throttle valve cavity, an O-shaped sealing ring 46 is sleeved outside the throttle valve 45, the throttle valve cavity is divided into a throttle valve front cavity 44 and a throttle valve back cavity 48, the front end of the throttle valve 45 is conical and corresponds to the throttle passage 43, and a through throttle valve inner passage 80 is arranged in the throttle valve 45; in this part, see the lower part of fig. 8, the throttle valve 45 is movable under pressure, and when the rear side pressure is high, the throttle valve 45 is pushed to move toward the connecting passage 43 until the connecting passage 43 is blocked by the taper of the front end of the throttle valve 45, and at this time, the connecting passage 43 and the throttle rear chamber 48 can only communicate with each other through the throttle inner passage 80 inside the throttle valve 45.

The reversing valve left oil chamber 53 is communicated with a bent pipe passage 57 in a bent pipe joint 56 through a fifth branch oil passage 54, and the bent pipe passage 57 is communicated with a hydraulic lock. This part is shown in the lower right of fig. 8.

The throttle passage 43 is communicated with a lower oil injection passage 63 in the U-shaped clamp 6 through an oil passage 42 and a sixth branch oil passage 59, and a lower oil nozzle 62 is arranged between the sixth branch oil passage 59 and the lower oil injection passage 63; see fig. 10 and 11 for this part. And finally communicates with the lower chamber of the hydraulic cylinder through the lower oil injection passage 63.

The reversing valve body front cavity 47 is communicated with an eighth branch oil passage 61 through a seventh branch oil passage 40, the eighth branch oil passage 61 is communicated with an upper oil injection passage 64 in the U-shaped clamp 6 through a ninth branch oil passage 66, and an upper oil injection nozzle 65 is arranged between the ninth branch oil passage 66 and the upper oil injection passage 64; the eighth bypass oil passage 61 communicates with an overflow mechanism through a tenth bypass oil passage 60, the overflow mechanism: the tenth branch oil path 60 is communicated with the overflow branch oil path 67, the overflow branch oil path 67 is communicated with the overflow valve cavity 26, an overflow valve spring 69 is arranged in the overflow valve cavity 26, the front end of the overflow valve spring 69 is propped against an overflow ball valve 68, the overflow ball valve 68 is arranged between the overflow valve cavity 26 and the overflow branch oil path 67, the diameter of the overflow ball valve 68 is larger than that of the overflow branch oil path 67, a pressure regulating push rod 71 is inserted into the rear end of the overflow valve spring 69, the rear end of the pressure regulating push rod 71 is propped against a pressure regulating nut 72, and the pressure regulating nut 72 is fixed in the overflow valve cavity 26; the overflow valve cavity 26 enters the oil suction passage 10 through the oil suction passage oil inlet 70; see fig. 10 and 11 for this part. The hydraulic cylinder is divided into two passages, the two passages are divided into an eighth branch oil passage 61, as shown in fig. 11, and the first passage is the left passage of the eighth branch oil passage 61 and is finally communicated with the upper cavity of the hydraulic cylinder through an upper oil injection passage 64; the second passage is a right passage of the eighth branch oil passage 61, and finally enters the lower section oil passage of the oil suction passage 10 through the overflow mechanism and the oil suction passage oil inlet 70.

The throttle front chamber 44 is communicated with the return oil path 16 through an eleventh branch oil path 73, and an oil return port throttle 11 is arranged at the oil outlet of the return oil path 16 and is communicated with the self-oil supply chamber 7. When the pressure of the front end of the throttle valve 45 is high, the hydraulic oil in the throttle channel 43 pushes the cone of the throttle valve 45 to be separated from the closed throttle channel 43, so that the throttle channel 43 is communicated with the throttle front cavity 44 and finally communicated with the oil self-supply cavity 7 through the return oil channel 16, as shown in fig. 12. The lower left corner of fig. 8 is not shown because the eleventh branch oil passage 73 is on the rear side of the throttle valve 45.

The long connecting shaft 8 is sleeved with the guide cover, the upper part of the guide cover is provided with the conical guide sleeve 77, the lower part of the guide cover is provided with the guide cover 78, and the outer edge 79 of the lower end of the guide cover 78 is clamped on the limit retainer ring 15 in the annular groove 76. As shown in fig. 16, because the eccentric cylinder 9 rotates eccentrically, a large amount of bubbles are generated by stirring the hydraulic oil nearby, and the bubbles gradually fill the self-supply chamber 7, and in order to prevent the bubbles from entering other parts of the self-supply chamber 7, a guide cover is provided, and the edge (outer edge 79) of the guide cover, the limit retainer 15 and the outer tile of the bearing 13 are simultaneously fixed in the annular groove 76, so that the guide cover 78 of the guide cover covers the vicinity of the upper end of the eccentric cylinder 9, and the tapered guide sleeve 77 covers the long connecting shaft 8 from bottom to top (the upper end is left to be communicated with the outside of the guide cover), so that even if bubbles are generated, the bubbles are basically in the guide cover, and a large part of the bubbles are basically ablated when reaching the top end of the tapered guide sleeve 77.

The working process of the invention is described below with reference to the accompanying drawings:

lifting process:

1. the motor 3 rotates clockwise, carrying the long shaft rod 8 and the eccentric cylinder 9 to rotate synchronously.

2. Hydraulic oil in the self-supply oil tank 4 enters from the oil suction passage 10, enters the reversing valve cavity 28 through the first transverse oil passage 25, and at the moment, the reversing valve 24 moves to the right side (the direction is shown to be upward in fig. 8), and the reversing valve plug 30 at the left side of the reversing valve 24 plugs the reversing valve cavity 28 and the reversing valve left side oil cavity 53.

3. The hydraulic oil continues to pass through the right oil chamber 31 of the reversing valve and the first branch oil passage 52 to enter the left oil dividing passage 32, and then enters the semicircular hole groove 17 on the right side (the upper side is seen in the direction in fig. 9) from the left longitudinal oil passage 20, and at this time, the region B of the eccentric cylinder 9 is located on the inner side of the inner shoe far away from the bearing 13, so that the piston pin 19 in the negative pressure piston pin hole 18 is in a thrown-out state, and the hydraulic oil from the semicircular hole groove 17 on the right enters the position where the piston pin 19 in the negative pressure piston pin hole 18 is left (i.e., the rear side of the piston pin 19), and because the eccentric cylinder 9 is rotated, the negative pressure piston pin hole 18 filled with hydraulic oil gradually approaches the inner wall of the inner shoe of the bearing 13, and at this time, the piston pin 19 is pushed into the inner side of the inner shoe of the negative pressure piston pin hole 18 until the inner wall of the inner shoe is completely relied on, and at this time, the rear side of the piston pin 19 is completely pushed out to the semicircular hole groove 17 on the left side (the lower side in the direction in fig. 9), and enters the right longitudinal oil passage 21, and then enters the throttle valve 43 to move forward through the throttle passage 45, and the throttle valve 43, and the throttle chamber 43 is closed in turn, and the throttle chamber 43 is closed.

4. Hydraulic oil that has entered the throttle passage 43 pushes away the ball seal 41 and flows into two oil passages (see fig. 10 and 11); the first oil passage: the hydraulic oil in the throttle channel 43 sequentially passes through the oil way 42, the sixth branch oil way 59, the lower oil spray nozzle 62, the lower oil spray way 63 and the lower cavity oil supply oil way in the U-shaped clamp 6 to enter the lower cavity of the hydraulic cylinder; the second oil path: pushing the ball seal 41 open, and enabling the hydraulic oil in the throttling channel 43 to sequentially enter an upper cavity of the hydraulic cylinder through a seventh branch oil circuit 40, an eighth branch oil circuit 61, a ninth branch oil circuit 66, an upper oil spray nozzle 65, an upper oil spray passage 64 and an upper cavity oil supply oil circuit in the U-shaped clamp 6; at the moment, the upper cavity and the lower cavity of the hydraulic cylinder form pressure difference (the pressure of the lower cavity is larger than that of the upper cavity), so that the hydraulic cylinder is pushed to rise, and the lifting function is realized.

5. Overflow process (see fig. 11 for this part): when the hydraulic oil pressure in the eighth branch oil passage 61, the tenth branch oil passage 60 and the overflow branch oil passage 67 is larger than the set pressure of the overflow valve, the overflow ball valve 68 is separated from the overflow branch oil passage 67, the overflow valve spring 69 is contracted, and the overflowed hydraulic oil sequentially enters the overflow valve cavity 26 and the oil suction passage oil inlet 70 from the overflow branch oil passage 67 and returns to the lower-section oil passage of the oil suction passage 10.

6. Hydraulic lock unlock (see lower right corner of fig. 8 for this section): the right oil distribution passage 50 simultaneously and sequentially feeds hydraulic oil from the third branch oil passage 51, the reversing valve left oil chamber 53, the fifth branch oil passage 54, and the elbow passage 57 in the elbow joint 56 into the hydraulic lock communication oil passage 55 to open the hydraulic lock.

The descending process comprises the following steps:

1. the motor 3 rotates anticlockwise and carries the long shaft lever 8 and the eccentric cylinder body 9 to rotate synchronously.

2. Hydraulic oil in the self-supply oil tank 4 enters from the oil suction passage 10, enters the reversing valve cavity 28 through the first transverse oil passage 25, and at the moment, the reversing valve 24 moves leftwards (the direction is shown as downwards in fig. 8), and a reversing valve blocking head 30 on the right side of the reversing valve 24 blocks the reversing valve cavity 28 from an oil cavity 31 on the right side of the reversing valve.

3. The hydraulic oil continues to enter the right oil dividing passage 50 through the left oil chamber 53 of the reversing valve and the third branch oil passage 51, then enters the left semicircular hole groove 17 (the lower side is seen in the direction in fig. 9) from the right longitudinal oil passage 21, enters the left longitudinal oil passage 20 through the negative pressure piston pin hole 18 (the working principle of the negative pressure piston pin hole 18 and the piston pin 19 is the same as that of the 3 rd step of the lifting process, except that the rotating direction of the eccentric cylinder 9 is different), then enters the reversing valve body rear cavity 37 through the left oil dividing passage 32 and the second branch oil passage 33 in sequence, and because the O-shaped sealing ring at the front end of the reversing valve body 36 seals the position between the reversing valve body rear cavity 37 and the reversing valve body front cavity 47, the hydraulic oil in the reversing valve body rear cavity 37 cannot directly enter the reversing valve body cavity 47, enters the reversing valve body cavity 38 through the reversing valve body through hole 34, then enters the reversing valve body cavity 38 front end, pushes the ball seal 41 to seal the reversing valve body front cavity 47 and seals the throttle channel 43, so that the hydraulic oil in the reversing valve body front cavity 47 sequentially pushes the seventh branch oil passage 40, the eighth branch oil passage 66, the ninth branch oil passage 66 and the oil supply channel 6, the oil injection cylinder upper oil injection cavity 65, and the oil injection cylinder upper-shaped oil injection cavity 6 lower oil injection cavity 65. At this time, the hydraulic oil in the lower chamber of the hydraulic cylinder enters the lower oil injection passage 63 through the lower chamber oil supply passage in the U-shaped clamp 6, and then enters the throttle passage 43 through the lower oil injection nozzle 62, the sixth branch oil passage 59 and the oil passage 42 in sequence, the hydraulic oil in the throttle passage 43 pushes the throttle valve 45 open so that the taper at the front end of the throttle valve 45 is separated from the blocking of the throttle passage 43, at this time, the hydraulic oil in the throttle passage 43 enters the throttle front chamber 44 (here, the throttle valve 45 of fig. 8 blocks the eleventh branch oil passage 73, the eleventh branch oil passage 73 cannot be shown in fig. 8, but the inlet end of the eleventh branch oil passage 73 is communicated with the throttle front chamber 44), the hydraulic oil in the throttle front chamber 44 enters the return oil passage 16 through the eleventh branch oil passage 73 (fig. 12), and flows back into the self-supply chamber 7 through the return port throttle valve 11 at the upper end of the return oil passage 16.

The overflow mechanism of the descending part is the same as the overflow mechanism (33 th stage) of the lifting mechanism, so that the description thereof is omitted here. The overflow valve (mechanism) plays a role of a safety valve, prevents the excessive pressure and protects the valve body and the sealing element.

Claims

1. An electrohydraulic cylinder, characterized in that: the motor (3) is arranged on the side surface of the hydraulic cylinder body (1), a buffer blocking piece (2) is arranged between the motor and the motor, the side surface of the pump body (5) is fixedly connected with the side surface of the U-shaped clamp (6) at the lower end of the hydraulic cylinder, and a sealed self-oil supply tank (4) is arranged between the motor (3) and the pump body (5); the upper half part of the pump body (5) is an oil self-supply mechanism, and the lower half part is a pump body oil way; the pump body (5) and the pump body protruding ring (12) are integrated to form the whole pump body;

the shaft of the motor (3) in the self-oil supply tank (4) is fixedly connected with the top end of the long connecting shaft (8), and the lower end of the long connecting shaft (8) is fixedly inserted into an inserting hole (23) at the top end of the eccentric cylinder body (9); the inside of the self-supply oil tank (4) is provided with a self-supply oil cavity (7);

self-oil supply mechanism: an oil supply groove (14) is formed in the upper half part of the pump body, and an oil distributing shaft mounting hole (27) is formed in the center of the lower half part of the pump body; the side wall of the oil supply groove (14) is provided with an annular groove (76); the eccentric cylinder body (9) is placed in the oil supply groove (14), the eccentric cylinder body (9) and the oil supply groove (14) are in an eccentric state, the lower surface of an outer tile of the bearing (13) is clamped on the lower edge (74) of the annular groove (76), the upper surface of the outer tile of the bearing (13) is tightly pressed through the limit check ring (15), and the upper end of the limit check ring (15) is clamped on the upper edge (75) of the annular groove (76);

the upper end of the oil distributing shaft (22) is inserted into an insertion hole at the lower end of the eccentric cylinder body (9) in a micro clearance fit manner, the lower end of the oil distributing shaft (23) is inserted into an oil distributing shaft mounting hole (27) in an interference fit manner, two semicircular hole grooves (17) with lateral openings are formed at the upper end of the oil distributing shaft (22), a negative pressure piston pin hole (18) is formed in the eccentric cylinder body (9) corresponding to the axial positions of the semicircular hole grooves (17), a piston pin (19) is placed in the negative pressure piston pin hole (18), two longitudinal oil passages, namely a left longitudinal oil passage (20) and a right longitudinal oil passage (21), are formed in the oil distributing shaft (22), the upper ends of the two longitudinal oil passages are respectively communicated with the two semicircular hole grooves (17), and the lower ends of the two longitudinal oil passages are respectively communicated with a left oil distributing passage (32) and a right oil distributing passage (50) in a pump body oil passage;

pump body oil circuit: an oil suction passage (10) is longitudinally formed in the pump body (5), the middle part of the oil suction passage (10) is communicated with a first transverse oil passage (25), the first transverse oil passage (25) is communicated with a reversing valve cavity (28), two ends of the reversing valve cavity (28) are respectively communicated with a reversing valve right oil cavity (31) and a reversing valve left oil cavity (53), the middle part of the reversing valve (24) is arranged in the reversing valve cavity (28), a reversing valve spring (29) is sleeved on a middle rod of the reversing valve (24), and two ends of the reversing valve spring (29) are respectively propped against the bottoms of reversing valve plugs (30) at two ends of the middle rod of the reversing valve (24);

the right oil cavity (31) of the reversing valve is communicated with the left oil distribution channel (32) through a first branch oil channel (52), the left oil distribution channel (32) is communicated with the reversing valve body rear cavity (37) through a second branch oil channel (33), the reversing valve body (36) is placed in the reversing valve body rear cavity (37), the rear end of the reversing valve body (36) is propped against the reversing valve body cavity plugging (35), the front end of the reversing valve body (36) is clamped at the joint of the reversing valve body front cavity (47) and the reversing valve body rear cavity (37), the reversing valve body (36) is sealed by an O-shaped sealing ring, the reversing valve body (36) is transversely provided with a reversing valve body through hole (34), the reversing valve body through hole (34) is communicated with the reversing valve body rear cavity (37) and the reversing valve body inner cavity (38), the front end of the reversing valve body inner cavity (38) is communicated with the reversing valve body front cavity (47), a guide spring (39) is arranged in the reversing valve body front cavity (47), the bottom end of the guide spring (39) is propped against the reversing valve body cavity plugging (35), the front end of the reversing valve body (47), the front end of the guide spring (39) is propped against the front end wall of the reversing valve body front end wall (47), and the diameter of the reversing valve body (41) is sealed by the guide ball sealing channel (41) and is large;

the left oil cavity (53) of the reversing valve is communicated with the right oil distribution passage (50) through a third branch oil passage (51), the right oil distribution passage (50) is communicated with the throttle valve rear cavity (48) through a fourth branch oil passage (49), a throttle valve (45) is arranged in the throttle valve cavity, an O-shaped sealing ring (46) is sleeved outside the throttle valve (45), the throttle valve cavity is divided into a throttle valve front cavity (44) and a throttle valve rear cavity (48), the front end of the throttle valve (45) is conical and corresponds to the throttle passage (43), and a through throttle valve inner passage (80) is formed in the throttle valve (45);

the left oil cavity (53) of the reversing valve is communicated with a bent pipe passage (57) in the bent pipe joint (56) through a fifth branch oil passage (54), and the bent pipe passage (57) is communicated with the hydraulic lock;

the throttle channel (43) is communicated with a lower oil injection passage (63) in the U-shaped clamp (6) through a sixth branch oil passage (59), and a lower oil injection nozzle (62) is arranged between the sixth branch oil passage (59) and the lower oil injection passage (63);

the reversing valve body front cavity (47) is communicated with an eighth branch oil way (61) through a seventh branch oil way (40), the eighth branch oil way (61) is communicated with an upper oil injection passage (64) in the U-shaped clamp (6) through a ninth branch oil way (66), and an upper oil injection nozzle (65) is arranged between the ninth branch oil way (66) and the upper oil injection passage (64); the eighth branch oil passage (61) is communicated with the overflow mechanism through a tenth branch oil passage (60), and the overflow mechanism is provided with: the tenth branch oil way (60) is communicated with the overflow branch oil way (67), the overflow branch oil way (67) is communicated with the overflow valve cavity (26), an overflow valve spring (69) is arranged in the overflow valve cavity (26), the front end of the overflow valve spring (69) is propped against an overflow ball valve (68), the overflow ball valve (68) is arranged between the overflow valve cavity (26) and the overflow branch oil way (67), the diameter of the overflow ball valve (68) is larger than the pipe diameter of the overflow branch oil way (67), a pressure regulating push rod (71) is inserted at the rear end of the overflow valve spring (69), the rear end of the pressure regulating push rod (71) is propped against a pressure regulating nut (72), and the pressure regulating nut (72) is fixed in the overflow valve cavity (26); the overflow valve cavity (26) enters the oil suction passage (10) through the oil suction passage oil inlet (70);

the throttle valve front cavity (44) is communicated with the return oil path (16) through an eleventh branch oil path (73), and an oil return port throttle valve (11) is arranged at an oil outlet of the return oil path (16) and is communicated with the self-supply oil cavity (7).

2. The electro-hydraulic cylinder as set forth in claim 1, wherein: a guide cover is sleeved outside the long connecting shaft (8), the upper part of the guide cover is a conical guide sleeve (77), the lower part of the guide cover is a guide cover (78), and the outer edge (79) of the lower end of the guide cover (78) is clamped on a limit retainer ring (15) in the ring groove (76).