CN112983773B - Automatic fluid supercharging device - Google Patents

Automatic fluid supercharging device Download PDF

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Publication number
CN112983773B
CN112983773B CN202110497814.0A CN202110497814A CN112983773B CN 112983773 B CN112983773 B CN 112983773B CN 202110497814 A CN202110497814 A CN 202110497814A CN 112983773 B CN112983773 B CN 112983773B
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China
Prior art keywords
fluid
spiral
piston rod
groove
plunger
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CN202110497814.0A
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Chinese (zh)
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CN112983773A (en
Inventor
王立峰
王秀强
李克旭
王孟晓
李武海
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Weifang Lichuang Electronic Technology Co Ltd
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Weifang Lichuang Electronic Technology Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/02—Pumping installations or systems having reservoirs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • F16J1/10—Connection to driving members
    • F16J1/12—Connection to driving members with piston-rods, e.g. rigid connections

Abstract

The invention provides an automatic fluid pressurization device, which comprises a reciprocating mechanism and a plunger and barrel assembly; the reciprocating mechanism comprises a cylinder body, a piston rod and a rotary return mechanism which is arranged on the cylinder body and used for applying return torque to the piston rod; the periphery of the piston is provided with a spiral ring groove and a spiral fluid groove communicated with a pressure cavity in the cylinder body; the cylinder body is provided with a fluid inlet hole, a fluid outlet hole and a fixing pin; the plunger and barrel assembly comprises a plunger sleeve provided with a low-pressure fluid inlet and a high-pressure fluid outlet and a plunger which is abutted with the piston rod and has a diameter smaller than that of the piston; under the action of the pressure cavity and the fluid in the plunger sleeve, the spiral ring groove is matched with the fixing pin to enable the piston rod to rotate and extend and enable the rotary return mechanism to generate return torque; when the piston rod extends in a forward rotation mode or retracts in a reverse rotation mode to a proper position, the return torque enables the piston rod to change the direction of rotation, and the communication state of the spiral fluid groove and the fluid inlet hole and the fluid outlet hole is switched; when the piston rod stretches out positively, the plunger pressurizes the fluid in the plunger sleeve. The invention has simple structure, low manufacturing cost and convenient arrangement.

Description

Automatic fluid supercharging device
Technical Field
The invention belongs to the technical field of fluid pressurization, and particularly relates to an automatic fluid pressurization device.
Background
In some fields, such as the field of oil lubrication systems for internal combustion engines, the pressure of oil is low, generally not exceeding 1MPa, and if the individual components in the oil lubrication system require high-pressure oil, a set of pumping devices is required, which is complicated in structure, high in cost and inconvenient to arrange. In view of the above, it is desirable to design an automatic fluid pressure increasing device, which is simple in structure, low in cost, easy to arrange, and particularly suitable for an internal combustion engine, so as to provide high-pressure fluid.
Disclosure of Invention
The present invention is directed to a fluid automatic supercharging device, which has a simple structure and a low manufacturing cost, and can provide high-pressure fluid, and is particularly suitable for use in an internal combustion engine.
In order to solve the problems in the prior art, the embodiment of the invention provides an automatic fluid pressurization device, which comprises a reciprocating mechanism and a plunger and barrel assembly; the reciprocating mechanism comprises a cylinder body, a piston and a piston rod, and a pressure cavity is formed between the piston and the cylinder body; the reciprocating mechanism further comprises a rotary return mechanism which is arranged on the cylinder body and used for applying return torque to the piston rod, a spiral ring groove and a spiral fluid groove which have the same spiral line trend are arranged on the periphery of the piston, and the spiral fluid groove is communicated with the pressure cavity; the cylinder body is provided with a fluid inlet hole, a fluid outlet hole and a fixing pin with one end extending into the spiral annular groove; the spiral fluid slot is selectively communicated with the fluid inlet hole or the fluid outlet hole;
the plunger and barrel assembly comprises a plunger sleeve and a plunger which is arranged in the plunger sleeve, is abutted against the piston rod and has a diameter smaller than that of the piston, and the plunger sleeve is provided with a low-pressure fluid inlet and a high-pressure fluid outlet which are communicated with an inner cavity of the plunger sleeve;
under the action of the fluid in the pressure cavity and the fluid in the plunger sleeve, the spiral ring groove is matched with the fixing pin, so that the piston rod rotates and extends relative to the cylinder body, and the rotary return mechanism generates the return torque; when the piston rod extends out of the position in a forward rotation mode or retracts back to the position in a reverse rotation mode, the piston rod changes the current steering direction under the action of the return torque, and the communication state of the spiral fluid groove and the fluid inlet hole and the fluid outlet hole is switched; when the piston rod stretches out in the forward rotation mode, the plunger piston pressurizes fluid in the plunger sleeve.
Further, the automatic fluid pressurization device further comprises a main inlet pipe, a first branch pipeline and a second branch pipeline which are communicated with the main inlet pipe in an intersecting manner, a pressure relief pipeline and a high-pressure supply pipeline, wherein the first branch pipeline is communicated with the fluid inlet, and the second branch pipeline is communicated with the low-pressure fluid inlet; the fluid outlet is communicated with the pressure relief pipeline, and the high-pressure fluid outlet is communicated with the high-pressure supply pipeline.
Furthermore, a first check valve is arranged on the second branch pipeline, a second check valve is arranged on the high-pressure supply pipeline, and an energy accumulator is arranged on the high-pressure supply pipeline at the downstream of the second check valve.
Further, the spiral ring groove comprises two spiral groove sections and two transverse groove sections connected between the two spiral groove sections; the spiral line direction of the spiral groove section is the same as that of the spiral fluid groove;
the spiral groove section is used for being matched with the fixing pin to realize the rotary extending or rotary retracting movement of the piston rod; the transverse groove section is used for being matched with the fixing pin to realize the communication between the spiral fluid groove and the fluid inlet hole or the fluid outlet hole.
Furthermore, two spiral ring grooves and two spiral fluid grooves are symmetrically arranged on the periphery of the piston;
one of the spiral fluid slots is selectively communicated with the fluid inlet hole or the fluid outlet hole; the cylinder body is provided with two fixing pins, and the fixing pins correspond to the spiral annular grooves one to one. Further, the reciprocating mechanism comprises a mounting seat and a deflector rod, the mounting seat is fixedly connected with the cylinder body, the deflector rod is axially connected with the piston rod in a sliding and synchronous rotating manner, and the deflector rod is axially limited on the mounting seat;
an arc-shaped groove unit is arranged on the mounting seat and comprises two arc-shaped guide grooves which are symmetrically arranged, and the circle center of each arc-shaped guide groove is concentric with the rotation center of the piston rod; each arc-shaped guide groove is internally provided with a sliding piece, a return elastic piece is arranged between the two sliding pieces, and one end part of the shifting lever is clamped between the two sliding pieces.
Further, the mounting seat comprises two limiting plates which are detachably connected and have the same structure; the arc-shaped groove unit is arranged on the limiting plate;
the slider is including being located two spacing axial region between the limiting plate with set up in the slip axial region of spacing axial region both sides, and two the slip axial region respectively with correspond on the limiting plate arc guide way looks adaptation.
Furthermore, the mounting seat is symmetrically provided with two arc-shaped groove units; correspondingly, the other end of the shifting lever is clamped between the two sliding pieces corresponding to the other arc-shaped groove unit.
Furthermore, two return elastic pieces are arranged between the two sliding pieces corresponding to the same arc-shaped groove unit, and the two return elastic pieces are respectively positioned on two sides of the mounting seat.
Further, the shifting lever comprises a connecting part and shifting parts arranged on two sides of the connecting part, a waist-shaped hole is formed in the connecting part, and the shifting parts are located between the two sliding parts; the piston rod comprises a profiling rod part matched with the waist-shaped hole.
Due to the adoption of the technical scheme, the invention has the following beneficial effects:
the invention relates to an automatic fluid supercharging device, which comprises a reciprocating mechanism and a plunger and barrel assembly; the reciprocating mechanism comprises a cylinder body, a piston and a piston rod, and a pressure cavity is formed between the piston and the cylinder body; the reciprocating mechanism also comprises a rotary return mechanism which is arranged on the cylinder body and used for applying return torque to the piston rod, the periphery of the piston is provided with a spiral ring groove and a spiral fluid groove which have the same spiral line trend, and the spiral fluid groove is communicated with the pressure cavity; the cylinder body is provided with a fluid inlet hole, a fluid outlet hole and a fixing pin; the spiral fluid groove is selectively communicated with the fluid inlet hole or the fluid outlet hole; the plunger matching part comprises a plunger sleeve and a plunger which is arranged in the plunger sleeve, is abutted to the piston rod and has a diameter smaller than that of the piston, and the plunger sleeve is provided with a low-pressure fluid inlet and a high-pressure fluid outlet which are communicated with the inner cavity of the plunger sleeve; under the action of fluid in the pressure cavity and fluid in the plunger sleeve, the spiral ring groove is matched with the fixing pin to enable the piston rod to do rotary telescopic motion relative to the cylinder body (the plunger piston does reciprocating motion relative to the plunger sleeve) and enable the rotary return mechanism to generate return torque; when the piston rod extends out in place in a forward rotation mode or retracts back in place in a reverse rotation mode, the piston rod changes the current steering direction under the action of the return torque, and the communication state of the spiral fluid groove and the fluid inlet hole and the fluid outlet hole is switched; when the piston rod stretches out positively, the plunger pressurizes the fluid in the plunger sleeve, and the fluid is pressurized by reciprocating motion.
In conclusion, the invention does not need a pumping device, and directly uses a reciprocating mechanism without a reversing valve to ensure that the plunger completes the pressurization of fluid in the plunger sleeve; compared with the prior art, the structure is simpler, the manufacturing cost is greatly reduced, and the arrangement is convenient.
Drawings
FIG. 1 is a partial cross-sectional view of an automatic fluid pressurization device of the present invention;
FIG. 2 is a schematic view of the reciprocating mechanism of FIG. 1;
FIG. 3 is an exploded view of the structure of FIG. 2;
FIG. 4 is a sectional view taken along A _ A in FIG. 1;
FIG. 5 is a schematic plan-view development of the piston of FIG. 3;
FIG. 6 is an exploded view of the first embodiment of the rotary return mechanism of FIG. 1;
FIG. 7 is a side view of a second embodiment of the rotary return mechanism of FIG. 1;
FIG. 8 is an exploded view of a second embodiment of the rotary return mechanism of FIG. 1;
FIG. 9 is a sectional view taken along line B _ B in FIG. 7;
10.1 and 10.2 are state reference diagrams of FIG. 9 when generating a return torque;
11.1-11.10 are schematic diagrams of the present invention implementing the reciprocating process;
in the figure: 1-cylinder body, 11-fluid inlet hole, 12-fluid outlet hole, 13-fixed pin, 2-piston, 21-spiral ring groove, 211-spiral groove section, 212-transverse groove section, 22-spiral fluid groove, 3-piston rod, 31-head, 32-profiling rod part, 4-pressure chamber, 5-rotary return mechanism, 51-mounting seat, 511-limiting plate, 5111-avoiding hole, 512-arc groove unit, 5121-arc guide groove, 513-first sliding part, 514-second sliding part, 5141-limiting shaft part, 5142-sliding shaft part, 515-return elastic part, 516-snap spring, 517-bearing, 518-return elastic part mounting hole, 52-deflector rod, 521-connecting part, 5211-waist-shaped hole, 522-toggle part, 6-plunger and barrel assembly, 61-plunger sleeve, 611-low pressure fluid inlet, 612-high pressure fluid outlet, 62-plunger, 7-main inlet pipe, 71-first branch pipeline, 72-second branch pipeline, 721-first one-way valve, 8-pressure relief pipeline, 9-high pressure supply pipeline, 91-second one-way valve, 92-energy accumulator and a-reciprocating mechanism.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments and orientations of "left", "right", "up", "down", etc. in the embodiments and examples described herein are merely illustrative and not restrictive.
The first embodiment is as follows:
as shown in fig. 1 to 4, the automatic fluid pressurization device disclosed in this embodiment includes a reciprocating mechanism a and a plunger and barrel assembly 6. The reciprocating mechanism a comprises a cylinder body 1, a piston 2 and a piston rod 3 connected with one end of the piston 2, and a pressure cavity 4 is formed between the other end of the piston 2 and the cylinder body 1. Besides, the reciprocating mechanism a further comprises a rotary return mechanism 5 which is arranged on the cylinder body 1 and is used for applying return torque to the piston rod 3, a spiral ring groove 21 and a spiral fluid groove 22 with the same spiral line trend are arranged on the periphery of the piston 2, and the opening end of the spiral fluid groove 22 is communicated with the pressure cavity 4; the cylinder body 1 is provided with a fluid inlet hole 11, a fluid outlet hole 12 and a fixing pin 13 with one end extending into the spiral ring groove 21; the spiral fluid slot 22 may be in communication with either the fluid inlet port 11 or the fluid outlet port 12, alternatively. The plunger and barrel assembly 6 comprises a plunger sleeve 61 and a plunger 62 which is axially and slidably arranged in the plunger sleeve 61 and is abutted to the piston rod 3, the diameter of the plunger 62 is smaller than that of the piston 2, and the plunger sleeve 61 is provided with a low-pressure fluid inlet 611 and a high-pressure fluid outlet 612 communicated with the inner cavity of the plunger sleeve; under the action of fluid in the pressure cavity 4 and fluid in the plunger sleeve 61, the spiral ring groove 21 is matched with the fixing pin 13 to enable the piston rod 3 (and the piston 2) to do rotary telescopic motion relative to the cylinder body 1 (meanwhile, the plunger 62 does axial reciprocating motion in the plunger sleeve 61) and enable the rotary return mechanism 5 to generate return torque; when the piston rod 3 extends out of the position in the forward rotation mode or retracts back to the position in the reverse rotation mode, the piston rod 3 changes the current steering direction under the action of the return torque, and the communication state of the spiral fluid groove 22 and the fluid inlet hole 11 and the fluid outlet hole 12 is switched; when the piston rod 3 extends in the forward direction, the plunger 62 pressurizes the fluid in the plunger sleeve 61.
The fluid is hydraulic oil, gas or engine oil and other media needing pressurization.
In this embodiment, the fluid automatic pressure increasing device further includes a main inlet pipe 7, a first branch pipeline 71 and a second branch pipeline 72 intersecting and communicating with the main inlet pipe 7, a pressure relief pipeline 8, and a high-pressure supply pipeline 9, where the first branch pipeline 71 communicates with the fluid inlet 11, and the second branch pipeline 72 communicates with the low-pressure fluid inlet 611; the fluid outlet 12 communicates with the pressure relief line 8, and the high-pressure fluid outlet 612 communicates with the high-pressure supply line 9.
In order to prevent the reverse flow, the second branch line 72 is provided with a first check valve 721, and the high-pressure supply line 9 is provided with a second check valve 91. In a further development, an accumulator 92 is provided in the high-pressure supply line 9 downstream of the second non-return valve 91 for temporarily storing redundant high-pressure fluid.
The supercharging principle is explained below on the basis of fig. 1; the diameter of the piston 2 is D and the diameter of the plunger 62 is D, D>d; the low pressure fluid pressure is P2, the high pressure fluid pressure is P1; when the low-pressure fluid is communicated with the fluid inlet hole 11, the acting force on the piston 2 is pi/4 XD2The direction is leftward; the forces of the low pressure fluid on the plunger 62 are: pi/4 xd2The direction is to the right; the resultant force is: pi/4 xD2-π/4×d2, the direction is to the left, the piston rod 3 pushes the plunger 62 to move to the left, and the fluid in the plunger sleeve 61 is pressurized, and the pressurization pressure is: p1= (pi/4 × D)2)/(π/4×d2)×P2=(D2)/(d2)×P2。
When the piston rod 3 extends in place in the forward rotation (pressurization is finished), the piston rod 3 changes the current steering direction under the action of the return torque, the spiral fluid groove 22 is switched from being communicated with the fluid inlet hole 11 to being communicated with the fluid outlet hole 12, and at the moment, the spiral fluid groove is communicated with the fluid inlet hole 11The force of the low pressure fluid on the piston 2 is 0 or close to 0, and the force of the low pressure fluid on the plunger 62 is: pi/4 xd2The direction is to the right; the resultant force is: pi/4 xd2And the direction is rightward, the plunger 62 pushes the piston 2 to move to the right and return.
As shown in fig. 5, the spiral ring groove 21 in the present embodiment includes two spiral groove segments 211 and two transverse groove segments 212 connected between the two spiral groove segments 211; the spiral groove segment 211 follows the same spiral as the spiral fluid groove 22. Wherein, the spiral groove section 211 is used for cooperating with the fixed pin 13 to realize the rotary extending or rotary retracting movement of the piston rod 3; the transverse groove section 212 is used for being matched with the fixed pin 13 to realize the communication of the spiral fluid groove 22 and the fluid inlet hole 11 or the fluid outlet hole 12, and further realize the reversing of the reciprocating motion.
In order to equalize the forces applied to the piston 2 to ensure the stable reliability of the reciprocating motion; in the embodiment, the piston 2 is further optimized, and two spiral ring grooves 21 and two spiral fluid grooves 22 are symmetrically arranged on the circumference of the optimized piston 2; one of the spiral fluid slots 22 is selectively in communication with either the fluid inlet aperture 11 or the fluid outlet aperture 12. Correspondingly, two fixing pins 13 are arranged on the cylinder body 1, and the fixing pins 13 correspond to the spiral ring grooves 21 one by one. When the fixing pin 13 is set to the dot-dash position, the rotary return mechanism 5 is set to the neutral position.
As shown in fig. 6, in the present embodiment, the rotary return mechanism 5 includes an installation seat 51 and a shift lever 52 which are integrated into a whole, the installation seat 51 is fixedly connected with the cylinder 1, the shift lever 52 is axially slidably and synchronously connected with the piston rod 3, and the shift lever 52 is axially limited on the installation seat 51; the mounting seat 51 is provided with an arc-shaped groove unit 512, the arc-shaped groove unit 512 comprises two arc-shaped guide grooves 5121 which are symmetrically arranged, and the circle center of each arc-shaped guide groove 5121 is concentric with the rotation center of the piston rod 3; each arc-shaped guide groove 5121 is provided with a sliding member (referred to as a first sliding member 513), a return elastic member 515 (preferably a spring) is disposed between the two first sliding members 513, and one end of the shift lever 52 is sandwiched between the two first sliding members 513. In the free state of the return elastic member 515, the distance between the two first sliding members 513 is S, and the width of one end of the shift lever 52 is S. Regardless of whether the plunger 52 (piston rod 3) rotates clockwise or counterclockwise, the plunger 52 and the piston rod 3 will receive a return torque to the neutral position by the return elastic member 515.
In this embodiment, a bearing 517 is disposed on the mounting seat 51, a cylindrical mounting portion is disposed on the shift lever 52, the cylindrical mounting portion is mounted in the bearing 517, and the purpose that the shift lever 52 is axially limited on the mounting seat 51 and rotates relative to the mounting seat is achieved by the bearing 517.
In some embodiments, the center of the mounting seat 51 is provided with an annular hole, the shifting rod 52 is provided with a cylindrical portion corresponding to the annular hole, and the cylindrical portions at two sides of the mounting seat 51 are provided with limiting members, so that the purpose that the shifting rod 52 is axially limited on the mounting seat 51 and rotates relatively is achieved; the structures for realizing axial limit are many, and are not listed here.
In this embodiment, in order to prevent the first sliding member 513 from moving axially on the mounting seat 51, a limiting structure (such as a snap spring 516) may be disposed on a portion of the first sliding member 513 protruding from both sides of the mounting seat 51.
In order to further ensure the stable reliability of the structure, the present embodiment is further optimized based on the above structure, and two arc-shaped slot units 512 are symmetrically arranged on the mounting seat 51; accordingly, the other end portion of the shift lever 52 is sandwiched between the two first sliding members 513 corresponding to the other arc-shaped slot unit 512.
In order to ensure that the rotary return mechanism 5 applies an effective return torque to the piston rod 3; in this embodiment, a further improvement is that two return elastic members 515 are disposed between two first sliding members 513 corresponding to the same arc-shaped slot unit 512, and the two return elastic members 515 are respectively located at two sides of the mounting base 51, that is, the portions of the first sliding members 513 extending out of the two sides of the mounting base 51 are both provided with return elastic member mounting holes 518.
Example two:
the second embodiment has substantially the same structure as the first embodiment, except that the rotary return mechanism 5 is adopted, so that the rotary return mechanism 5 in the second embodiment is more convenient to assemble and has a simple assembly mode. Only the differences will be described in detail below.
As shown in fig. 7 to 9 and fig. 10.1 and 10.2, the optimized mounting seat 51 has a split structure, and includes two limiting plates 511 (circular limiting plates) detachably connected by a pin and having the same structure; the two arc-shaped groove units 512 are arranged on the limiting plate 511; a slider (referred to as a second slider 514) is disposed in each of the arc-shaped guide grooves 5121. The second slider 514 is axially restrained by means of two restraining plates 511; the second sliding member 514 includes a limiting shaft portion 5141 located between the two limiting plates 511 and sliding shaft portions 5142 disposed at two sides of the limiting shaft portion 5141, the two sliding shaft portions 5142 are respectively matched with the arc-shaped guiding grooves 5121 of the corresponding limiting plates 511, and the portions of the sliding shaft portions 5142 extending out of the arc-shaped guiding grooves 5121 of the corresponding limiting plates 511 are provided with return elastic member mounting holes 518.
In this embodiment, the shift lever 52 includes a connecting portion 521 and shift portions 522 disposed at two sides of the connecting portion 521, the connecting portion 521 is provided with a waist-shaped hole 5211, and the shift portions 522 are located between two second sliding members 514 in the same arc-shaped slot unit 512; the piston rod 3 comprises a head 31 fixedly connected with the piston 2 and a profiling rod 32 which is matched with the waist-shaped hole 5211 to realize axial sliding and synchronous rotating connection. The limiting plate 511 is provided with an avoiding hole 5111 in the center thereof, which is matched with the connecting part 521.
In other embodiments, the shift lever 52 and the piston rod 3 are connected in an axially sliding and synchronous rotating manner through other structures such as a key connection structure or a linear bearing structure; and will not be described in detail herein.
The operating principle of the reciprocating mechanism a is briefly explained below based on the above description:
shown collectively in fig. 1, 5, 11.1 through 11.10; for ease of understanding, the up-and-down motion directions shown in fig. 11.1 to 11.10 correspond to the axial reciprocating motion of the piston rod 3 and the piston 2 in the implementation application; the corresponding left and right movements in the figure correspond to the rotational movements of the piston rod 3 and the piston 2 in the implementation application. Fig. 11.1-11.6 are movement diagrams (i.e., movement diagrams corresponding to the pressurization process) for overcoming the fluid pressure in plunger sleeve 61 under the action of the pressure generated by the fluid in pressure chamber 4; fig. 11.7-11.10 are views of the movement of the piston 2 under the force of the fluid pressure in the plunger sleeve 61.
Here, as shown in fig. 11.1, when the rotary return mechanism 5 is at the neutral position, the return torque is zero, and the spiral fluid groove 22 is communicated with the fluid inlet hole 11. As shown in fig. 11.2 to 11.4, under the action of the fluid in the pressure chamber 4 and the fluid pressure in the plunger sleeve 61 (the pressure of the fluid in the pressure chamber 4 to the piston 2 is greater than the pressure of the fluid in the plunger sleeve 61 to the plunger 62, see the above description of the pressurization principle), one spiral groove section 211 in the spiral annular groove 21 cooperates with the fixing pin 13 to make the piston rod 3 (the piston 2) perform forward rotation and extension movement relative to the cylinder 1 (the schematic direction in the drawing is that the piston 2 moves downward and leftward relative to the cylinder 1, and the plunger 62 starts to pressurize the fluid in the plunger sleeve 61), and make the rotary return mechanism 5 generate a return torque (rightward). As shown in fig. 11.5 to 11.6, when the piston rod 3 is extended forward to a certain position (pressurization is completed), i.e. the fixing pin 13 is located in one of the transverse groove sections 212, the piston rod 3 changes the current direction to start reverse rotation (the piston 2 moves to the right relative to the cylinder 1 in the direction indicated by the drawing) under the action of the return torque of the rotary return mechanism 5, the spiral fluid groove 22 is switched from communicating with the fluid inlet hole 11 to communicating with the fluid outlet hole 12, and the fixing pin 13 is located at the end of the other spiral groove section 211.
As shown in fig. 11.7 to 11.9, under the action of the fluid in plunger sleeve 61 (the fluid enters plunger sleeve 61 through second branch line 72 and low-pressure fluid inlet 611, the pressure of the fluid in plunger sleeve 61 on plunger 62 is greater than the pressure of the fluid in pressure chamber 4 on piston 2, and plunger 62 exerts the pressure on piston rod 3 to retract it), another spiral groove section 211 cooperates with fixed pin 13 to start reverse retraction of piston rod 3 (the schematic direction in the figure is that piston 2 moves upward and rightward relative to cylinder 1), and to generate the return torque (leftward) by rotary return mechanism 5. As shown in fig. 11.10, when the piston rod 3 is reversely rotated and retracted to the right, i.e. the fixing pin 13 is located in the other transverse groove section 212, the piston rod 3 changes the current direction to start the forward rotation (the piston 2 moves leftwards relative to the cylinder 1 in the schematic direction in the figure) under the action of the return torque of the rotary return mechanism 5, and the spiral fluid groove 22 is switched from being communicated with the fluid outlet hole 12 to being communicated with the fluid inlet hole 11; under the action of the fluid in the pressure chamber 4 and the fluid pressure in the plunger sleeve 61 (the pressure of the fluid in the pressure chamber 4 to the piston 2 is greater than the pressure of the fluid in the plunger sleeve 61 to the plunger 62), the piston rod 3 starts to rotate forwards and extends out (the state shown in figure 11.1, and the pressurizing process is started again); the reciprocating motion is carried out in such a way as to realize fluid pressurization.
In conclusion, the invention does not need a pumping device, and directly uses a reciprocating mechanism without a reversing valve to ensure that the plunger completes the pressurization of the fluid in the plunger sleeve; compared with the prior art, the structure is simpler, the manufacturing cost is greatly reduced, and the arrangement is convenient.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.

Claims (10)

1. An automatic fluid pressurization device comprises a reciprocating mechanism and a plunger and barrel assembly; the reciprocating mechanism comprises a cylinder body, a piston and a piston rod, and a pressure cavity is formed between the piston and the cylinder body; the reciprocating mechanism is characterized by further comprising a rotary return mechanism which is arranged on the cylinder body and used for applying return torque to the piston rod, wherein the periphery of the piston is provided with a spiral ring groove and a spiral fluid groove which have the same spiral line trend, and the spiral fluid groove is communicated with the pressure cavity; the cylinder body is provided with a fluid inlet hole, a fluid outlet hole and a fixing pin with one end extending into the spiral annular groove; the spiral fluid slot is selectively communicated with the fluid inlet hole or the fluid outlet hole;
the plunger and barrel assembly comprises a plunger sleeve and a plunger which is arranged in the plunger sleeve, is abutted against the piston rod and has a diameter smaller than that of the piston, and the plunger sleeve is provided with a low-pressure fluid inlet and a high-pressure fluid outlet which are communicated with an inner cavity of the plunger sleeve;
under the action of the fluid in the pressure cavity and the fluid in the plunger sleeve, the spiral ring groove is matched with the fixing pin, so that the piston rod rotates and extends relative to the cylinder body, and the rotary return mechanism generates the return torque; when the piston rod extends out of the position in a forward rotation mode or retracts back to the position in a reverse rotation mode, the piston rod changes the current steering direction under the action of the return torque, and the communication state of the spiral fluid groove and the fluid inlet hole and the fluid outlet hole is switched; when the piston rod stretches out in the forward rotation mode, the plunger piston pressurizes fluid in the plunger sleeve.
2. The automatic fluid pressurization device according to claim 1, further comprising a main inlet, a first branch line and a second branch line in intersection communication with the main inlet, a pressure relief line, and a high pressure supply line, wherein the first branch line is in communication with the fluid inlet, and the second branch line is in communication with the low pressure fluid inlet; the fluid outlet is communicated with the pressure relief pipeline, and the high-pressure fluid outlet is communicated with the high-pressure supply pipeline.
3. The automatic fluid pressurization device according to claim 2, characterized in that a first check valve is provided on the second branch line, a second check valve is provided on the high-pressure supply line, and an accumulator is provided on the high-pressure supply line downstream of the second check valve.
4. The automatic fluid pressurization device according to claim 1, characterized in that said helical ring groove comprises two helical groove segments and two transverse groove segments connected between said two helical groove segments; the spiral line direction of the spiral groove section is the same as that of the spiral fluid groove;
the spiral groove section is used for being matched with the fixing pin to realize the rotary extending or rotary retracting movement of the piston rod; the transverse groove section is used for being matched with the fixing pin to realize the communication between the spiral fluid groove and the fluid inlet hole or the fluid outlet hole.
5. The automatic fluid pressurization device according to claim 1 or 4, characterized in that the periphery of the piston is symmetrically provided with two spiral ring grooves and two spiral fluid grooves;
one of the spiral fluid slots is selectively communicated with the fluid inlet hole or the fluid outlet hole; the cylinder body is provided with two fixing pins, and the fixing pins correspond to the spiral annular grooves one to one.
6. The automatic fluid pressurization device according to claim 1, wherein the reciprocating mechanism comprises a mounting seat and a deflector rod, the mounting seat is fixedly connected with the cylinder body, the deflector rod is axially connected with the piston rod in a sliding and synchronous rotating manner, and the deflector rod is axially limited on the mounting seat;
an arc-shaped groove unit is arranged on the mounting seat and comprises two arc-shaped guide grooves which are symmetrically arranged, and the circle center of each arc-shaped guide groove is concentric with the rotation center of the piston rod; each arc-shaped guide groove is internally provided with a sliding piece, a return elastic piece is arranged between the two sliding pieces, and one end part of the shifting lever is clamped between the two sliding pieces.
7. The automatic fluid pressurization device according to claim 6, characterized in that, the mounting seat comprises two removably connected limiting plates with the same structure; the arc-shaped groove unit is arranged on the limiting plate;
the slider is including being located two spacing axial region between the limiting plate with set up in the slip axial region of spacing axial region both sides, and two the slip axial region respectively with correspond on the limiting plate arc guide way looks adaptation.
8. The automatic fluid pressurization device according to claim 6 or 7, characterized in that two arc-shaped groove units are symmetrically arranged on the mounting seat; correspondingly, the other end of the shifting lever is clamped between the two sliding pieces corresponding to the other arc-shaped groove unit.
9. The automatic fluid pressurization device according to claim 8, wherein two return elastic members are disposed between two sliding members corresponding to the same arc-shaped slot unit, and the two return elastic members are respectively located at two sides of the mounting seat.
10. The automatic fluid pressurization device according to claim 6, wherein said lever comprises a connecting portion and a toggle portion disposed on both sides of said connecting portion, said connecting portion having a waist-shaped hole, said toggle portion being located between two of said sliding members; the piston rod comprises a profiling rod part matched with the waist-shaped hole.
CN202110497814.0A 2021-05-08 2021-05-08 Automatic fluid supercharging device Active CN112983773B (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1361494A (en) * 1971-06-21 1974-07-24 Trw Inc Hydraulic servomotor controllers
FR2982332B1 (en) * 2011-11-08 2013-11-22 Valeo Embrayages TORQUE TRANSMISSION ASSEMBLY, IN PARTICULAR FOR MOTOR VEHICLE
CN104141595A (en) * 2014-07-23 2014-11-12 上海帕格液压设备有限公司 Pneumatic hydraulic pump
CN204877548U (en) * 2015-05-29 2015-12-16 王力丰 System for economy utilizes compressed air for automotive power source
CN107687456A (en) * 2016-08-04 2018-02-13 大连精维液压技术有限公司 A kind of special high pulling torque rotary type joint power device
CN108716334A (en) * 2018-06-28 2018-10-30 黄庆盛 A kind of self-return damping door hinge
CN111075706B (en) * 2019-12-26 2023-10-31 宁波真格液压科技有限公司 Control valve for reciprocating pump and reciprocating pump comprising same

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