CN110821781A

CN110821781A - Hydraulic air compressor

Info

Publication number: CN110821781A
Application number: CN201911362473.5A
Authority: CN
Inventors: 陈艳艳
Original assignee: Ningbo Wen Fan Electrical And Mechanical Technology Development Co Ltd
Current assignee: Ningbo Wen Fan Electrical And Mechanical Technology Development Co Ltd
Priority date: 2019-12-26
Filing date: 2019-12-26
Publication date: 2020-02-21

Abstract

The invention belongs to the technical field of air compressors. The invention discloses a hydraulic air compressor driven by hydraulic pressure, which comprises a shell, a main piston, a first piston and a steering sleeve, wherein a control chamber and a first air chamber which are mutually independent are arranged in the shell, the main piston is positioned in the control chamber, the first piston is positioned in the first air chamber, the steering sleeve is positioned between the shell and the main piston and can reciprocate relative to the shell along with the reciprocating movement of the main piston, so that the switching between a first station and a second station is realized, two sides of the main piston are respectively and alternately communicated with high-pressure oil, and a buffer oil way and a one-way valve are arranged between the first air chamber and an oil return box. The hydraulic air compressor can perform air compression work under the driving of hydraulic pressure, has simple and compact structure and low manufacturing cost, can eliminate impact collision during reversing, and prolongs the service life.

Description

Hydraulic air compressor

Technical Field

The invention belongs to the technical field of air compressors, and particularly relates to a hydraulic air compressor driven by hydraulic pressure.

Background

The air compressor is a reciprocating compressor, and realizes compression work on air through reciprocating movement. At present, the common air compressor mainly has the following structural forms:

the first is a structural form of compressing gas by utilizing a common rotating motor and driving a piston to reciprocate in a cylinder body through a crank connecting rod mechanism. When the piston performs a compression stroke, the suction valve is closed, and the exhaust valve is opened; when the piston performs a suction stroke, the exhaust valve closes and the intake valve opens. The compressor with the structure form has the advantages of small working compression ratio, short stroke of reciprocating motion, high vibration and noise during working and easy abrasion, and the structure of changing rotary motion into linear motion is complex, the efficiency is low, and the noise during working of the mechanical transmission mechanism is high. Meanwhile, there is an impact collision of the piston with the cylinder when the piston moves to the end, thereby causing collision noise and collision damage.

The second is a linear compressor configuration. Most of the existing linear compressors adopt a single stator coil structure, and the linear compressor adopting the structure needs to realize reciprocating motion of a rotor in the linear compressor to compress gas, and generally needs to be reset by virtue of the restoring force of a spring after the rotor completes a compression stroke. However, the linear compressor of this structure has a drawback of low system efficiency because the use of the spring increases the resistance when the piston moves and does not compress air any more during the mover restoring process.

The third is the screw air compressor structure. The screw air compressor is not only difficult to process, needs special lubricating oil to lubricate and seal during working, but also can be used after the compressed air obtained from the screw air compressor is subjected to oil-gas separation treatment, and high-pressure air cannot be provided.

Disclosure of Invention

In order to solve the problems of low working efficiency, large energy consumption and high cost of the air compressor with the structural form, the invention provides a hydraulic air compressor driven by hydraulic pressure. The hydraulic air compressor comprises a shell, a main piston, a first one-way valve and a steering sleeve, wherein the main piston is fixedly connected with the first piston and moves synchronously;

the inside of the shell is provided with a control chamber and a first air chamber which are mutually independent, and the shell is provided with a port P1, a port P2, a port T1, a port T2, a first air inlet, a first air outlet and a first buffer oil way;

the master piston is located in the control chamber and divides the control chamber into a first control chamber and a second control chamber; the P1 port and the T1 port are positioned on one side of the first control chamber, and the P2 port and the T2 port are positioned on one side of the second control chamber;

the first piston is located in the first air chamber and divides the first air chamber into a first working air chamber and a first auxiliary air chamber; the first air inlet and the first air outlet are simultaneously communicated with the first working air chamber;

the steering sleeve is positioned between the shell and the main piston and is provided with a first oil port, a second oil port, a third oil port and a fourth oil port; the steering sleeve can reciprocate relative to the shell along with the axial reciprocating movement of the main piston and is switched between a first station and a second station; in the first station, the first oil port is communicated with a P1 port, the fourth oil port is communicated with a T2 port, and the second oil port, the third oil port, a P2 port and a T1 port are kept closed; in the second station, the second oil port is communicated with a P2 oil port, the third oil port is communicated with a T1 port, and the first oil port, the fourth oil port, a P1 port and a T2 port are kept closed;

one end of the first buffer oil path is communicated with a port T1, the other end of the first buffer oil path is communicated with the first auxiliary air chamber, and the end of the first buffer oil path is positioned in a contact area of the first piston and the shell when the first air chamber finishes air suction operation; the first check valve is connected with the valve body, an inlet of the first check valve is communicated with a T1 port, and an outlet of the first check valve is communicated with the first auxiliary air chamber along the axial direction.

Preferably, the steering sleeve is connected with the housing in a rotating manner relative to the circumferential direction, and when the main piston reciprocates axially, the steering sleeve rotates in a reciprocating manner relative to the housing in the circumferential direction to switch between the first station and the second station.

Preferably, the hydraulic air compressor is provided with two control rods, and two ends of the steering sleeve are respectively provided with an inner spiral groove; the control rods are positioned at the end part of the control chamber, the horizontal sections of the two control rods are axially opposite to the main piston and can perform axial reciprocating linear motion, and the vertical sections of the two control rods are respectively connected with the two inner spiral grooves and can perform reciprocating sliding along the inner spiral grooves.

Further preferably, the housing is provided with a guide hole and a guide groove, and the guide hole and the guide groove are respectively used for installing the horizontal section and the vertical section of the control rod, so that the vertical section of the control rod keeps axially reciprocating.

Further preferably, one end of the guide hole is communicated with the first control chamber (or the second control chamber), and the other end is communicated with the first auxiliary air chamber (or the second auxiliary air chamber); the horizontal section of the control rod is positioned in the guide hole and forms an axial reciprocating sliding seal.

Preferably, the hydraulic air compressor is also provided with a positioning component; the positioning assembly is located between the shell and the steering sleeve and used for positioning a first station and a second station of the steering sleeve.

Further preferably, the positioning assembly comprises a positioning hole, a positioning spring, a positioning ball and a positioning groove; the positioning hole and the positioning groove are respectively positioned on the shell and the steering sleeve, and the positioning spring and the positioning ball are positioned in the positioning hole; when the steering sleeve is positioned between the first station and the second station, one end of the positioning ball is positioned in the positioning hole, and the other end of the positioning ball extends into the positioning groove.

11. Preferably, the hydraulic air compressor further comprises a second piston and a second one-way valve, a second air chamber which is mutually independent from the control chamber and the first air chamber is further arranged in the shell, and a second air inlet hole, a second air outlet hole and a second buffer oil path are further formed in the shell; the second piston is fixedly connected with the main piston and moves synchronously;

the second piston is located in the second gas chamber and divides the second gas chamber into a second working gas chamber and a second auxiliary gas chamber; the second air inlet hole and the second air outlet hole are simultaneously communicated with the second working air chamber;

one end of the second buffer oil path is communicated with a port T2, the other end of the second buffer oil path is communicated with the second auxiliary air chamber and is positioned in a contact area of the second piston and the valve body when the second air chamber finishes air suction operation; the second one-way valve is connected with the valve body, an inlet of the second one-way valve is communicated with a T2 port, and an outlet of the second one-way valve is communicated with the second auxiliary air chamber along the axial direction.

Further preferably, the first piston and the second piston are located on both sides of the main piston, and the first air chamber and the second air chamber are located on both sides of the control chamber.

Preferably, the shell adopts a split structure, a partition plate is arranged inside the shell, and the inside of the shell is divided into a control chamber and a first air chamber which are distributed along the axial direction.

Compared with the air compressor with the existing structure, the hydraulic air compressor has the following beneficial technical effects:

1. in the invention, a P1 port and a P2 port which are connected with a hydraulic pump and a T1 port and a T2 port which are connected with an oil return tank are respectively arranged in control chambers at two sides of a main piston, so that the main piston is driven by hydraulic pressure to move axially, a first piston and a second piston are driven to respectively perform compressed air work in a first air chamber and a second air chamber, and meanwhile, the main piston is used for performing alternate switching control on a steering sleeve between two stations in the axial moving process, so that the steering sleeve is used for finishing alternate conversion of hydraulic pressure applied to two sides of the main piston by hydraulic oil, the main piston is driven to perform axial reciprocating alternate movement, and the alternate compressed air work of the first piston and the second piston under the hydraulic drive is finished. Therefore, the compressed air which takes hydraulic pressure as power to drive the first piston and the second piston does work, complex mechanical structures such as a motor, a crank-link mechanism and the like in the existing air compressor are replaced, the structure is simplified, the compactness of the volume is improved, mechanical transmission parts and special requirements on sealing are omitted, and mechanical noise and cost are reduced.

2. In the invention, the automatic switching of the stations is realized by controlling the action of the steering sleeve in the reciprocating movement process of the main piston, so that the continuous reciprocating compressed air acting of the hydraulic air compressor can be completely realized only by controlling the oil liquid conveying switching between the port P1 and the port P2, thereby reducing the control requirement and improving the convenience of operation and control.

3. In the invention, a first buffer oil path and a first check valve which are communicated with the first auxiliary air chamber and the T1 port, and a second buffer oil path and a second check valve which are communicated with the second auxiliary air chamber and the T2 port are arranged. Therefore, in the reciprocating movement process of the main piston, the hydraulic buffer brake of the piston in the movement process is realized by utilizing the position change between the first piston and the first buffer oil way and the position change between the second piston and the second buffer oil way, so that the impact collision between the piston and the shell when the piston moves to the terminal position and the noise generated by the impact collision are avoided. Meanwhile, the first check valve and the second check valve can be used for avoiding the phenomenon of suction in the first auxiliary air chamber and the second auxiliary air chamber when the first piston and the second piston move reversely, so that the operation stability and the service life of the whole hydraulic air compressor are further improved.

Drawings

Fig. 1 is a schematic structural view illustrating a process of moving a hydraulic air compressor to a direction of a second air chamber according to the embodiment;

fig. 2 is a schematic structural diagram of the hydraulic air compressor of the present embodiment moving toward the second air chamber to contact the second control rod;

fig. 3 is a schematic structural diagram of the hydraulic air compressor of the embodiment when moving to the direction of the second air chamber and the first piston covers the first buffer oil path;

fig. 4 is a schematic structural view illustrating the hydraulic air compressor of the present embodiment moving to the terminal position in the direction of the second air chamber;

fig. 5 is a schematic structural view illustrating a process of moving the hydraulic air compressor to the first air chamber in the embodiment;

fig. 6 is a schematic structural view illustrating the hydraulic air compressor of the present embodiment moving toward the first air chamber to contact the first control rod;

fig. 7 is a schematic structural diagram illustrating the hydraulic air compressor of the present embodiment moving to the first air chamber to cover the second buffer oil path by the second piston;

fig. 8 is a schematic structural view illustrating the hydraulic air compressor of the present embodiment moving to the terminal position in the direction of the first air chamber;

FIG. 9 is a schematic structural diagram of the steering sleeve in the present embodiment;

FIG. 10 is a schematic view of the outer structure of the partition board in this embodiment;

FIG. 11 is a partial schematic view of the mounting of the locating assembly between the spacer and the steering sleeve.

Detailed Description

The technical solution of the present invention will be further described in detail with reference to the accompanying drawings and embodiments.

Referring to fig. 1, the hydraulic air compressor of the present embodiment includes a housing 1, a main piston 2, a first piston 3, a second piston 4, a steering sleeve 5, a first check valve 6 and a second check valve 7, wherein the main piston 2, the first piston 3 and the second piston 4 are coaxially and fixedly connected, and can perform synchronous reciprocating linear motion in an axial direction.

The casing 1 is a hollow structure, a control chamber 11, a first air chamber 12 and a second air chamber 13 which are mutually independent are arranged in the casing 1, the first air chamber 12 and the second air chamber 13 are respectively positioned at two sides of the control chamber 11, and a P1 port, a P2 port, a T1 port, a T2 port, a first air inlet 14, a first air outlet 15, a second air inlet 16, a second air outlet 17, a first buffer oil path 18 and a second buffer oil path 19 are arranged on the casing 1. Wherein, corresponding ventilation one-way valves are respectively arranged in the first air inlet hole 14, the first exhaust hole 15, the second air inlet hole 16 and the second exhaust hole 17, so that corresponding one-way air inlet and one-way exhaust functions of the air holes are realized.

The master piston 2 is located in the control chamber 11 and divides the control chamber 11 into a first control chamber 111 and a second control chamber 112. Wherein, the port P1 and the port T1 are positioned at one side of the first control room 111, and the port P2 and the port T2 are positioned at one side of the second control room 112.

The first piston 3 is located in the first gas chamber 12, and divides the first gas chamber 12 into a first working gas chamber 121 and a first auxiliary gas chamber 122. Wherein the first air intake hole 14 and the first air exhaust hole 15 are simultaneously communicated with the first working air chamber 121.

The second piston 4 is located in the second air chamber 13, and divides the second air chamber 13 into a second working air chamber 131 and a second auxiliary air chamber 132. Wherein the second suction hole 16 and the second discharge hole 17 are simultaneously communicated with the second working air chamber 131.

The steering sleeve 5 is sleeved between the housing 1 and the main piston 2, and is provided with a first oil port 51, a second oil port 52, a third oil port 53 and a fourth oil port 54 penetrating through the wall thickness thereof. Wherein, the steering sleeve 5 can perform reciprocating rotation relative to the circumferential direction of the shell 1 along with the axial reciprocating movement of the main piston 2, thereby realizing the reciprocating switching between the first station and the second station.

When the steering sleeve 5 is in the first station, the first oil port 51 is communicated with the port P1, the fourth oil port 54 is communicated with the port T2, and the second oil port 52, the third oil port 53, the port P2 and the port T1 are kept closed. At this time, the oil in the port P1 flows to the first control chamber 111 through the first oil port 51, and the oil in the second control chamber 112 flows to the port T2 through the fourth oil port 54, so as to drive the main piston 2 to move toward the second air chamber 13, and further drive the second piston 4 to perform air compression work in the second air chamber 13, and drive the first piston 3 to perform air suction operation in the first air chamber 12.

When the steering sleeve 5 is in the second station, the second oil port 52 is communicated with the P2 oil port, the third oil port 53 is communicated with the T1 port, and the first oil port 51, the fourth oil port 54, the P1 port and the T2 port are kept closed. At this time, the oil in the port P2 flows to the second control chamber 112 through the second oil port 52, and the oil in the first control chamber 111 flows to the port T1 through the third oil port 53, so as to drive the main piston 2 to move toward the first air chamber 12, and further drive the first piston 3 to perform air compression work in the first air chamber 12, and drive the second piston 4 to perform air suction operation in the second air chamber 13.

The first check valve 6 is connected to the valve body 1, and an inlet of the first check valve 6 communicates with the port T1, and an outlet of the first check valve 6 communicates with the first auxiliary air chamber 122 in the axial direction. At this time, when the main piston 2 moves in the direction of the first air chamber 12 and the first cushion oil passage 18 is in the closed state, the oil at the port T1 may flow into the first auxiliary air chamber 122 through the first check valve 6, thereby preventing the first auxiliary air chamber 122 from being sucked empty.

The second check valve 7 is connected to the valve body 1, and an inlet of the second check valve 7 communicates with the port T2, and an outlet of the second check valve 7 communicates with the second auxiliary air chamber 132 in the axial direction. At this time, when the main piston 2 moves in the direction of the second air chamber 13 and the second cushion oil passage 19 is in the closed state, the oil at the port T2 can flow into the second auxiliary air chamber 132 through the second check valve 7, thereby preventing the second auxiliary air chamber 132 from being evacuated.

One end of the first buffer oil passage 18 communicates with the port T1, and the other end communicates with the first auxiliary air chamber 122 and is located in a contact area of the first piston 3 and the housing 1 when the first air chamber 12 completes the air suction operation. At this time, in the process that the first piston 3 moves in the direction of the second air chamber 13 along with the main piston 2, before the main piston 2 and the first piston 3 move to the terminal positions, the first piston 3 forms a covering seal for the first buffer oil passage 18 in advance, so that the first auxiliary air chamber 122 forms a sealed space, thereby instantly increasing the oil pressure in the first auxiliary air chamber 122 which is not discharged to the T1 port through the first buffer oil passage 18, further forming a reverse braking force for the first piston 3, and realizing hydraulic buffer braking for the main piston 2 and the first piston 3 and the second piston 4.

One end of the first cushion oil passage 19 communicates with the port T2, and the other end communicates with the second auxiliary air chamber 132 and is located in a contact area of the second piston 4 and the housing 1 when the second air chamber 13 completes the suction operation. At this time, in the process that the second piston 4 moves in the direction of the first air chamber 12 along with the main piston 2, before the main piston 2 and the second piston 4 move to the terminal positions, the second piston 4 forms a covering seal for the second buffer oil passage 19 in advance, so that the second auxiliary air chamber 132 forms a sealed space, the oil pressure in the second auxiliary air chamber 132, which is not discharged to the port T2 through the second buffer oil passage 19, is instantly increased, the reverse braking force for the second piston 4 is formed, and the hydraulic buffer braking for the main piston 2 and the first piston 3 and the second piston 4 is realized.

As shown in fig. 1 and 9, two control rods 8 are provided in the hydraulic air compressor of the present embodiment, and inner spiral grooves 55 are provided at both end portions of the steering sleeve 5, respectively. The two control rods 8 are respectively located at the ends of the first control chamber 111 and the second control chamber 112, and meanwhile, the horizontal sections of the two control rods 8 correspond to the main piston 2 along the axial direction and can perform axial reciprocating linear motion, and the vertical sections of the two control rods 8 are respectively connected with the two inner spiral grooves 55 and can perform relative reciprocating sliding along the inner spiral grooves 55, so as to drive the steering sleeve 5 to rotate in the circumferential direction.

When the steering sleeve is positioned at the first station, the main piston moves towards the second air chamber and moves for a certain distance to be in contact with the horizontal section of the control rod in the second control chamber, so that the control rod is driven to axially move towards the second air chamber together, the vertical section of the control rod and the inner spiral groove slide relatively, the steering sleeve is driven to rotate in the circumferential direction, and the steering sleeve is gradually switched to the second station. Meanwhile, in the process that the steering sleeve rotates in the circumferential direction, the control rod in the first control chamber can be driven to axially move in the direction of the second air chamber.

Similarly, when the steering sleeve is located at the second station, the main piston moves towards the first air chamber and moves for a certain distance to be in contact with the horizontal section of the control rod in the first control chamber, so that the control rod is driven to axially move towards the first air chamber together, the vertical section of the control rod and the inner spiral groove slide relatively, the steering sleeve is driven to rotate in the circumferential direction, and the steering sleeve is gradually switched to the first station. Meanwhile, in the process that the steering sleeve rotates in the circumferential direction, the control rod in the second control chamber is driven to axially move along the direction of the first air chamber.

At this time, along with the axial reciprocating movement of the main piston, the control rod is used for completing the synchronous switching control of the steering sleeve between the first station and the second station, so that the synchronous switching among the P1 port, the P2 port, the T1 port, the T2 port, the first oil port 51, the second oil port 52, the third oil port 53 and the fourth oil port 54 is realized.

As shown in fig. 1 and 6, in the present embodiment, the two partition plates 9 are provided inside the casing 1, so that the inside of the casing 1 is divided into the first air chamber 12, the control chamber 11, and the second air chamber 13, which are sequentially distributed in the axial direction. Meanwhile, the partition board 9 is provided with a guide hole 91 and a guide groove 92 for installing the horizontal section and the vertical section of the control rod 8, respectively, and the guide groove 92 arranged axially is utilized to limit the axial guidance of the vertical section in the control rod 8, so that the vertical section of the control rod 8 can keep axial reciprocating linear motion, and the steering sleeve 5 can rotate in a reciprocating manner along the circumferential direction. Similarly, in other embodiments, the horizontal sections of the control rod and the guide hole can also be directly designed into a polygonal cross-sectional shape, so that the guide limitation of the guide groove on the vertical section in the control rod is omitted, and the axial reciprocating linear motion of the vertical section in the control rod is also realized.

Further, in the present embodiment, the guide hole 91 has a through hole structure, i.e., one end is communicated with the first control chamber 111 (or the second control chamber 112), and the other end is communicated with the first auxiliary air chamber 122 (or the second auxiliary air chamber 132) through the partition plate 9. At this moment, the horizontal section of the control rod is positioned in the guide hole and performs the reciprocating axial movement process, one end of the horizontal section, which is positioned in the first control chamber (or the second control chamber), can bear the hydraulic pressure of high-pressure oil, and one end of the horizontal section, which is positioned in the first auxiliary air chamber (or the second auxiliary air chamber), can bear the hydraulic pressure of backflow oil, so that hydraulic pressure difference exists at the two ends of the horizontal section. Therefore, when the main piston stops moving continuously due to the fact that oil pressure on two sides of the main piston is exchanged, the control rod can move continuously under the action of the hydraulic pressure difference between two ends of the main piston until the control rod reaches the terminal end, station switching of the steering sleeve is completed, and the control rod can be stably kept at the terminal end position under the action of the hydraulic pressure difference between two ends of the control rod before the main piston moves reversely to be in contact with another control rod, so that the position stability of the steering sleeve in the stage is maintained, and the auxiliary positioning effect is achieved.

Similarly, in other embodiments, the guide hole may also be a blind hole structure, and during the process of making the horizontal section of the control rod located in the guide hole perform reciprocating movement, both ends of the horizontal section are kept in a communication state, that is, hydraulic pressures applied to both ends of the horizontal section are kept in an equal state. Therefore, in the process that the main piston drives the control rod to move, when the control rod drives the steering sleeve to rotate to the oil hydraulic pressure in the first control chamber and the oil hydraulic pressure in the second control chamber to be adjusted, the main piston gradually stops to continue to move under the action of the hydraulic pressure on the two sides, and at the moment, even if the hydraulic pressures of the two ends of the horizontal section in the control rod are the same, the control rod can also continue to move under the action of inertia force until the control rod reaches the terminal, and station switching of the steering sleeve is completed.

In this embodiment, although a scheme that the control rod drives the steering sleeve to rotate in the circumferential direction is adopted, the steering sleeve is switched between the first station and the second station. However, in other embodiments, the steering sleeve may be switched between the first station and the second station in other manners, for example, the steering sleeve may be designed in a sliding valve structure, and after the positional relationship among the first oil port, the second oil port, the third oil port, and the fourth oil port is adjusted, the steering sleeve may also be driven by two control rods to perform axial reciprocating linear movement, so as to complete on-off adjustment among the P1 port, the P2 port, the T1 port, the T2 port, the first oil port, the second oil port, the third oil port, and the fourth oil port, and thus, the steering sleeve is switched between the first station and the second station.

In addition, the reciprocating motion of the steering sleeve can be completed even in an auxiliary electric control mode. For example, a displacement sensor is arranged at the end of the axial reciprocating movement of the main piston, the position of the main piston is detected by the displacement sensor, and the motor is controlled to drive the steering sleeve to perform reciprocating rotation along the circumferential direction or reciprocating movement along the axial direction, so that the switching of the stations of the steering sleeve is completed.

In other embodiments, according to different requirements of design and working conditions, a positioning assembly can be further arranged between the partition plate and the steering sleeve and used for performing auxiliary positioning on the position of the steering sleeve when the steering sleeve is switched to the first station and the second station, so that the steering sleeve can be accurately and stably fixed on the first station and the second station.

As shown in fig. 11, the positioning assembly may be composed of a positioning hole 101, a positioning spring 102, a positioning ball 103, and a positioning groove 104. Wherein, a positioning hole 101 is opened on the partition plate 9, and a positioning spring 102 and a positioning ball 103 are positioned in the positioning hole 101, and a positioning groove 104 is positioned on the steering sleeve 5 and on the same circumference corresponding to the positioning hole 101. In this way, during the switching process of the steering sleeve 5 between the first station and the second station, the positioning ball 103 directly contacts with the end face of the steering sleeve 5 to compress the positioning spring 102, so as to be held in the positioning hole 101, when the steering sleeve 5 is switched to the first station and the second station, the positioning groove 104 and the positioning hole 101 are on the same axis, one end of the positioning ball 103 is located in the positioning hole 101 under the action of the positioning spring 102, and the other end extends out of the positioning groove 104, so that the position fixing between the partition plate 9 and the steering sleeve 5 is completed, and the auxiliary positioning of the steering sleeve 5 is realized.

Similarly, in other embodiments, the positioning hole can be arranged on the steering sleeve, and the positioning groove can be arranged on the partition plate, even other structures such as a positioning pin are adopted to realize the position fixing and auxiliary positioning of the steering sleeve.

In addition, in this embodiment, the first piston and the second piston are respectively arranged on two sides of the main piston, and the first air chamber and the second air chamber are respectively arranged on two sides of the control chamber, so that the alternating compressed air of the first air chamber and the second air chamber acts in the reciprocating process of the main piston, and the efficiency of compressed air is improved. However, in other embodiments, the hydraulic air compressor can be designed to have only the first piston and the first air chamber according to different working conditions, so that the volume of the whole air compressor is reduced, and a structural form of unidirectional compressed air acting is formed. Even, the first piston and the second piston are sequentially arranged on the same side of the main piston, and the first air chamber and the second air chamber are arranged on the same side of the control chamber, so that a one-way compressed air work doing mode with double air chambers is formed, and the one-way compressed air work doing efficiency is improved.

In addition, as shown in fig. 1, in the present embodiment, the housing 1 is of a split structure, and is composed of three housings corresponding to the control chamber 11, the first air chamber 12 and the second air chamber 13, and the two partition plates 9 and the three housings are axially and fixedly connected by bolts. Like this, not only be convenient for to whole casing manufacturing, reduce the processing degree of difficulty and cost, convenient to detach improves the convenience of packaging efficiency and maintenance moreover.

Referring to fig. 1 to 8, when the hydraulic air compressor of the present embodiment is operated, the P1 port and the P2 port are connected to the hydraulic pump, and the T1 port and the T2 port are connected to the oil return tank, and the specific operation process is as follows:

when the steering sleeve 5 is in the first station, the first oil port 51 is communicated with the port P1, the fourth oil port 54 is communicated with the port T2, and the second oil port 52, the third oil port 53, the port P2 and the port T1 are kept closed. At this time, the high-pressure oil output from the hydraulic pump flows into the first control chamber 111 through the port P1 and the first port 51, and the oil in the second control chamber 112 flows back to the tank through the fourth port 54 and the port T2. The main piston 2 starts to move towards the second air chamber 13 under the action of the high-pressure oil in the first control chamber 111, drives the second piston 4 to perform air compression work in the second air chamber 13 and output high-pressure air through the second exhaust hole 17, and drives the first piston 3 to perform air suction operation in the first air chamber 12 and introduce air through the first air suction hole 14. Meanwhile, the oil in the first auxiliary air chamber 122 flows back to the oil return tank through the first buffer oil passage 18 and the port T1, and the oil in the oil return tank flows into the second auxiliary air chamber 132 through the port T2 and the first buffer oil passage 19, so as to prevent the second auxiliary air chamber 132 from being vacuumed.

When the main piston 2 moves into contact with the control rod 8 in the second control chamber 112, it starts to move with it, driving the steering sleeve 5 in rotation and starting the switch to the second position. In the process, the port P1 and the first port 51 are gradually closed, the port P2 and the second port 52 are gradually communicated, high-pressure oil starts to enter the second control chamber 112 through the port P2, the port T1 and the third port 53 are gradually communicated, the port T2 and the fourth port 54 are gradually closed, and the oil in the first control chamber 111 starts to flow back to the oil tank through the port T1. At this time, the force applied to the main piston 2 by the oil in the first control chamber 111 gradually decreases, the force applied to the main piston 2 by the oil in the second control chamber 112 gradually increases, the hydraulic pressure difference between both sides of the main piston 2 starts to gradually decrease, but the main piston 2 continues to move in the direction of the second air chamber 13.

When the first piston 3 moves to cover and seal the first buffer oil path 18 along with the main piston 2, the first auxiliary air chamber 122 forms a closed space, and the pressure of the oil which does not flow out to the oil return tank rises instantly, so that reverse hydraulic pressure is formed for the first piston 3, hydraulic buffer braking for the main piston 2 and the first piston 3 is achieved, and impact collision between the main piston 2 and the first piston 3 and the partition plate 9 is avoided.

When the main piston stops moving continuously towards the direction of the second air chamber and is separated from the contact with the control rod in the second control chamber under the hydraulic pressure difference between the two sides of the main piston and the hydraulic buffer braking action of the hydraulic oil in the first auxiliary air chamber, the control rod in the second control chamber continues moving under the hydraulic pressure difference between the two ends of the control rod until the control rod is contacted with the partition plate and the steering sleeve is completely switched to the second station.

When the steering sleeve 5 is in the second station, the second oil port 52 is communicated with the port P2, the third oil port 53 is communicated with the port T1, and the first oil port 51, the fourth oil port 54, the port P1 and the port T2 are kept closed. At this time, the high-pressure oil output from the hydraulic pump flows into the second control chamber 112 through the port P2 and the port 52, and the oil in the first control chamber 111 flows back to the tank through the port 53 and the port T1. The main piston 2 starts to move towards the first air chamber 12 under the action of the high-pressure oil in the second control chamber 112, drives the first piston 3 to perform air compression work in the first air chamber 12 and output high-pressure air through the first exhaust hole 15, and drives the second piston 4 to perform air suction operation in the second air chamber 13 and introduce air through the second air suction hole 17.

In this process, when the first buffer oil passage 18 is in the covering state, the first check valve 6 is opened, the oil in the oil return tank flows into the first auxiliary air chamber 122 through the port T1 and the first check valve 6, so as to prevent the first auxiliary air chamber 122 from being vacuumed, and after the first buffer oil passage 18 is uncovered along with the movement of the first piston 3, the oil in the oil return tank directly flows into the first auxiliary air chamber 122 through the first buffer oil passage 18. At the same time, the oil in the second auxiliary air chamber 132 returns to the oil return tank through the second buffer oil passage 19 and the port T2.

When the main piston 2 moves into contact with the control rod 8 in the first control chamber 111, it starts to move with it, driving the steering sleeve 5 in rotation and starting the switch to the first position. In the process, the port P2 and the port second port 52 are gradually closed, the port P1 and the port first port 51 are gradually communicated, high-pressure oil starts to enter the first control chamber 111 through the port P1, the port T1 and the port third port 53 are gradually closed, the port T2 and the port fourth port 54 are gradually communicated, and the oil in the second control chamber 112 starts to flow back to the oil tank through the port T2. At this time, the force applied to the main piston 2 by the oil in the first control chamber 111 gradually increases, the force applied to the main piston 2 by the oil in the second control chamber 112 gradually decreases, and the hydraulic pressure difference between both sides of the main piston 2 starts to gradually decrease, but the main piston 2 continues to move in the direction of the first air chamber 12.

When the second piston 4 moves to cover and block the second buffer oil path 19 along with the main piston 2, the second auxiliary air chamber 132 forms a closed space, and the pressure of the oil which does not flow out to the oil return tank rises instantly, so that reverse hydraulic pressure is formed for the second piston 4, hydraulic buffer braking for the main piston 2 and the second piston 4 is achieved, and impact collision between the main piston 2 and the second piston 4 and the partition plate 9 is avoided.

When the main piston stops moving continuously towards the direction of the first air chamber and is separated from the contact with the control rod in the first control chamber under the hydraulic pressure difference between the two sides of the main piston and the hydraulic buffer braking action of hydraulic oil in the second auxiliary air chamber, the control rod in the first control chamber continues moving under the hydraulic pressure difference between the two ends of the control rod until the control rod is contacted with the partition plate and the steering sleeve is completely switched to the first station.

And the reciprocating action is repeated in sequence to finish the work of reciprocating compressed air of the hydraulic air compressor under the hydraulic drive. The P1 port and the P2 port can be respectively connected with two hydraulic pumps, can also be connected with the same hydraulic pump by means of a reversing valve, and are matched with the reciprocating movement of the main piston by controlling the reversing operation of the reversing valve, so that the hydraulic air compressor is ensured to work by reciprocating compressed air under the hydraulic drive.

Claims

1. A hydraulic air compressor is characterized by comprising a shell, a main piston, a first one-way valve and a steering sleeve, wherein the main piston is fixedly connected with the first piston and moves synchronously;

2. The hydraulic air compressor as claimed in claim 1, wherein the steering sleeve is rotatably connected to the housing in a circumferential direction, and the steering sleeve is rotated in a circumferential direction relative to the housing during the axial reciprocating movement of the main piston to switch between the first position and the second position.

3. The hydraulic air compressor as claimed in claim 2, wherein the hydraulic air compressor is provided with two control rods, and the two ends of the steering sleeve are respectively provided with an inner spiral groove; the control rods are positioned at the end part of the control chamber, the horizontal sections of the two control rods are axially opposite to the main piston and can perform axial reciprocating linear motion, and the vertical sections of the two control rods are respectively connected with the two inner spiral grooves and can perform reciprocating sliding along the inner spiral grooves.

4. The hydraulic air compressor as claimed in claim 3, wherein the housing has a guide hole and a guide groove for receiving the horizontal and vertical sections of the control rod, respectively, such that the vertical section of the control rod is maintained to reciprocate axially.

5. The hydraulic air compressor as claimed in claim 4, wherein one end of the guide hole is communicated with the first control chamber (or the second control chamber) and the other end is communicated with the first auxiliary air chamber (or the second auxiliary air chamber); the horizontal section of the control rod is positioned in the guide hole and forms an axial reciprocating sliding seal.

6. The hydraulic air compressor of claim 1, further comprising a positioning assembly; the positioning assembly is located between the shell and the steering sleeve and used for positioning a first station and a second station of the steering sleeve.

7. The hydraulic air compressor as claimed in claim 6, wherein the positioning assembly includes a positioning hole, a positioning spring, a positioning ball and a positioning groove; the positioning hole and the positioning groove are respectively positioned on the shell and the steering sleeve, and the positioning spring and the positioning ball are positioned in the positioning hole; when the steering sleeve is positioned between the first station and the second station, one end of the positioning ball is positioned in the positioning hole, and the other end of the positioning ball extends into the positioning groove.

8. The hydraulic air compressor as claimed in any one of claims 1 to 7, further comprising a second piston and a second check valve, wherein a second air chamber independent from the control chamber and the first air chamber is further provided inside the housing, and a second air inlet hole, a second air outlet hole and a second buffer oil path are further provided on the housing; the second piston is fixedly connected with the main piston and moves synchronously;

9. The hydraulic air compressor of claim 8, wherein the first and second pistons are located on opposite sides of the main piston, and the first and second air chambers are located on opposite sides of the control chamber.

10. The hydraulic air compressor as claimed in any one of claims 1 to 7, wherein the housing is of a split type structure, and a partition is provided inside the housing to divide the inside of the housing into a control chamber and a first air chamber, which are axially distributed.