TWI512204B - Diaphragm compressor oil pump structure and diaphragm compressor - Google Patents

Description

Pump oil structure of diaphragm compressor and diaphragm compressor

The present invention relates to a diaphragm compressor, and more particularly to a pump oil structure of a diaphragm compressor and a diaphragm compressor having the same.

Diaphragm compressors have high compression ratio characteristics and are widely used for gas compression to generate high pressure or even liquefy gases for various industrial applications.

The diaphragm compressor reciprocally drives the piston through the crankshaft and the connecting rod, and indirectly drives the diaphragm to bulge or contract with the hydraulic oil body to compress and transport the gas. During the diaphragm bulging process, part of the hydraulic oil body will be returned to the oil storage tank through the oil discharge check valve, or used to lubricate the crankshaft, connecting rod and other parts. When the diaphragm is retracted, the pump oil pump passes through the pressure regulating valve, and the hydraulic oil body is pumped from the oil reservoir to the piston and the diaphragm.

The pump oil pumping setup takes up extra space, increases diaphragm compression manufacturing costs, and increases the complexity of the mechanism. Due to the setting of the pump oil pump, the diaphragm compressor is not easy to be miniaturized.

In view of the problem that the oil returning and oil replenishing mechanism of the conventional diaphragm compressor is too large, the diaphragm compressor is not easy to be miniaturized, and the present invention proposes a pump oil structure, which has the characteristics of simple structure and small volume.

The invention discloses a pump oil structure of a diaphragm compressor, comprising a sliding sleeve and a Piston, an oil check valve, and a return pipe. The diaphragm compressor has a diaphragm compression assembly.

The sliding sleeve has a hollow pipe connected to the diaphragm compression assembly; wherein the hollow pipe comprises a first passage and a second passage, the first passage has a larger diameter than the second passage, and the second passage connects the diaphragm compression assembly.

The piston has a first compression portion and a second compression portion; wherein the diameter of the first compression portion is greater than the second compression portion, and the first compression portion reciprocates in the first passage, thereby driving the second compression portion to the second passage Reciprocating movement, and a sealing structure is disposed between the first compression portion and the first passage.

The oil discharge check valve is connected to the first passage of the hollow pipe and is located between the sealing structure and the second passage for unidirectionally moving the hydraulic oil body away.

One end of the return pipe is connected to the diaphragm compression assembly for receiving the hydraulic oil body.

When the piston moves toward the diaphragm compression assembly, a difference in diameter between the first compression portion and the second compression portion causes a volume effect to drive the hydraulic oil body to exit through the oil discharge check valve; when the piston is away from the diaphragm compression assembly, The difference in diameter between the first compression portion and the second compression portion causes a volume effect, and drives the hydraulic oil body to be replenished to the diaphragm compression assembly through the oil return pipe.

The invention also discloses a diaphragm compressor comprising at least two diaphragm compression assemblies, at least two pairs of sliding sleeves, a piston assembly, two oil outlet check valves, and two return oil pipes.

Each of the sliding sleeves has a hollow tube, and the hollow tube is connected to one of the diaphragm compression assemblies; wherein the hollow tube comprises a first passage and a second passage, the first passage has a larger diameter than the second passage, and the second passage Connect the corresponding diaphragm compression assembly.

The piston assembly has two pistons interlocking with each other; wherein each piston has a first compression portion and a second compression portion; wherein the diameter of the first compression portion is greater than the second compression portion, and the first pressure Retracting portion reciprocates in the first passage, thereby driving the second compression portion to reciprocate in the second passage, and a sealing structure is disposed between the first compression portion and the first passage; the oil discharge check valve is respectively connected to The first passage of each hollow pipe is located between the sealing structure and the second passage for unidirectionally moving the hydraulic oil body of the corresponding diaphragm compression assembly.

One end of each return pipe is connected to one of the two diaphragm compression assemblies, and the other end is connected to an oil discharge check valve corresponding to the other diaphragm compression assembly for receiving the hydraulic oil body.

Wherein, when the piston moves toward the diaphragm compression assembly, the difference in diameter between the first compression portion and the second compression portion causes a volume effect, and drives the hydraulic oil body to exit through the oil discharge check valve; when the piston is away from the diaphragm compression assembly When the diameter difference between the first compression portion and the second compression portion causes a volume effect, the hydraulic oil body is driven to replenish through the oil return pipe to the diaphragm compression assembly.

The pump oil structure of the diaphragm compressor of the invention achieves oil return and oil replenishment through the operation of the piston, and does not require an additional pump to drive the hydraulic oil body, thereby simplifying the structure and reducing the cost, thereby further effectively The space for the temporary use of the diaphragm compressor is reduced, which is advantageous for miniaturization of the diaphragm compressor.

100‧‧‧ pump oil structure

110‧‧‧Sleeve

112‧‧‧ hollow pipe

112a‧‧‧First Passage

112b‧‧‧second channel

120‧‧‧Piston

120a‧‧‧First compression department

120b‧‧‧Second compression department

120c‧‧‧ Sealing structure

130‧‧‧Oil check valve

140‧‧‧pressure regulator

150‧‧‧ return pipe

210‧‧‧Hydraulic cylinder

212‧‧‧ openings

220‧‧‧Separator

300‧‧‧ oil storage tank

400‧‧‧Piston assembly

1000‧‧‧diaphragm compressor

Fig. 1 is a schematic cross-sectional view showing a diaphragm compressor according to an embodiment of the present invention.

2 and 3 are schematic cross-sectional views showing a structure of a pump oil according to an embodiment of the present invention.

Referring to FIG. 1 , FIG. 2 and FIG. 3 , the pump oil structure 100 disclosed in the embodiment of the present invention is applied to a diaphragm compressor 1000 for compressing gas. Producing high pressure gas or liquefying the gas: The foregoing functions are merely examples, and other modes of use are not excluded.

Referring to FIG. 2 , the pump oil structure 100 includes a sliding sleeve 110 , a piston 120 , an oil discharge check valve 130 , a pressure regulating valve 140 , and a return oil pipe 150 .

As shown in FIG. 2, the sliding sleeve 110 has a hollow conduit 112 that is coupled to a diaphragm compression assembly 200. The hollow duct 112 includes a first passage 112a and a second passage 112b. The first passage 112a is larger in diameter than the second passage 112b, and the second passage 112b is connected to the diaphragm compression assembly 200.

The diaphragm compression assembly 200 includes a hydraulic cylinder 210 and a diaphragm 220. The hydraulic cylinder 210 is connected to the second passage 112b of the hollow duct 112, and the hydraulic cylinder 210 has an opening 212. The diaphragm 220 closes the opening 212, and the hydraulic oil body is driven by the reciprocating movement of the piston 120, and the diaphragm 220 is bulged or retracted outward to drive the gas compression mechanism.

The piston 120 has a first compression portion 120a and a second compression portion 120b. The diameter of the first compression portion 120a is larger than that of the second compression portion 120b. A sealing structure 120c is disposed between the first compression portion 120a and the first passage 112a to prevent leakage of the hydraulic oil body between the first compression portion 120a and the first passage 112a. In general, the seal structure 120c is an oil seal ring, but other forms of seal structure 120c are not excluded. The first compression portion 120a reciprocates in the first passage 112a, thereby driving the second compression portion 120b to reciprocate in the second passage 112b, and driving the hydraulic oil body to flow through the second passage 120a and the diaphragm compression assembly 200.

The oil discharge check valve 130 is connected to the first passage 112a of the hollow pipe 112 and between the seal ring 120c and the second passage 112b for unidirectionally moving the hydraulic oil body of the diaphragm compression assembly 200 away from the hollow pipe 112.

The pressure regulating valve 140 is connected to the hydraulic cylinder 210 of the diaphragm compression assembly 200 to overflow the hydraulic oil body to an oil reservoir 300 when the pressure exceeds a predetermined pressure.

One end of the oil return pipe 150 is connected to the oil pressure cylinder 210 of the diaphragm compression assembly 200, and the other end is connected to the oil discharge check valve 130 of the other pump oil structure 100, thereby receiving the hydraulic oil released by the other pump oil structure 100. body.

The oil discharge check valve 130 and the oil return pipe 150 constitute a mechanism for the hydraulic oil body to enter and exit, and the hydraulic fluid passes at different times to generate oil and oil replenishment. The timing of the operation of the oil check valve 130 and the oil return pipe 150 will be continuously described below.

As shown in FIG. 2, when the piston 120 moves toward the diaphragm compression assembly 200 and the diaphragm 220 is bulged outward, the difference in diameter between the first compression portion 120a and the second compression portion 120b causes a volume effect, which drives the original position. The hydraulic oil body between the seal ring 120c and the second passage 112b is pressed and exits through the oil discharge check valve 130. Since the oil discharge check valve 130 is connected to the oil return pipe 150 of the other set of the pump oil structure 100, the separated hydraulic oil body can be directly replenished to the other set of the diaphragm 220 by the oil return pipe 150 of the other set of the pump oil structure 100. The indented diaphragm compresses the assembly 200.

In the compression process, if the pressure is higher than a set value, the pressure regulating valve 140 will be opened, and excessive oil body will pass and overflow to the oil storage tank 300.

As shown in FIG. 3, when the diaphragm 120 is retracted away from the diaphragm compression assembly 200, the difference in diameter between the first compression portion 120a and the second compression portion 120b will cause the seal ring 120c and the second passage 112b to be The hydraulic oil body that generates an oil storage space S and the oil return pipe 150 is replenished by the oil discharge check valve 130 of the other pump oil structure 100.

As shown in FIG. 1, two sets of pump oil structures 100, or even multiple sets of pump oil structures 100, may constitute a diaphragm compressor 1000. Taking the two sets of pump oil structure 100 as an example, the diaphragm compressor 1000 includes two diaphragm compression assemblies 200, two pairs of sliding sleeves 110, two oil outlet check valves 130, two pressure regulating valves 140, and two oil return pipes 150, An oil reservoir 300 and a piston assembly 400.

Each of the sliding sleeves 110 has a hollow duct 112 that connects one of the two diaphragm compression assemblies 200. The hollow duct 112 includes a first passage 112a and a second passage 112b. The first passage 112a has a larger diameter than the second passage 112b, and the second passage 112b connects the diaphragm compression assembly 200. The oil discharge check valve 130 is connected to the first passage 112a of the hollow pipe 112 and between the seal ring 120c and the second passage 112b for unidirectionally moving the hydraulic oil body of the diaphragm compression assembly 200 away from the hollow pipe 112.

The pressure regulating valve 140 is connected to the hydraulic cylinder 210 of the diaphragm compression assembly 200 to overflow the hydraulic oil body to an oil reservoir 300 when the pressure exceeds a predetermined pressure.

One end of the oil return pipe 150 is connected to the oil pressure cylinder 210 of the diaphragm compression assembly 200, and the other end is connected to the oil discharge check valve 130 of the other pump oil structure 100, thereby receiving the hydraulic oil released by the other pump oil structure 100. body.

As shown in Fig. 1, the difference between the two sets of diaphragm compression assemblies 200 is that the right side diaphragm compression assembly 200 of the oil discharge check valve 130 is connected to the oil return tube 150 of the left diaphragm compression assembly 200; The oil discharge check valve 130 of the membrane compression assembly 200 is connected to the return oil pipe 150 of the diaphragm compression assembly 200 on the right side.

The piston assembly 400 has two pistons 120 that are interlocked with each other. The two pistons 120 can be two ends of a single rod, and can also be connected through two independent components of a crankshaft and a connecting rod. Each piston 120 has a first compression portion 120a and a second compression portion 120b. The first compression portion 120a has a larger diameter than the second compression portion 120b, and the first compression portion 120a reciprocates in the first passage 112a, thereby driving the second compression portion 120b to reciprocate in the second passage 112b, and the first compression portion A sealing structure 120c is disposed between the 120a and the first passage 112a. As described above, when the piston 120 moves toward the diaphragm compression assembly 200, the difference in diameter between the first compression portion 120a and the second compression portion 120b causes a volume effect, and the displacement The hydraulic oil body is separated from the oil discharge check valve 130; when the piston 120 is away from the diaphragm compression assembly 200, the difference in diameter between the first compression portion 120a and the second compression portion 120b causes a volume effect, and drives the hydraulic oil body through the oil return pipe 150 replenishment to diaphragm compression assembly 200.

The pump oil structure of the diaphragm compressor achieves oil return and oil replenishment through the operation of the piston, and does not require an additional pump to drive the hydraulic oil body, thereby simplifying the structure and reducing the cost, thereby further effectively reducing the size. The temporary space of the diaphragm compressor is beneficial to the miniaturization of the diaphragm compressor.

100‧‧‧ pump oil structure

110‧‧‧Sleeve

112‧‧‧ hollow pipe

112a‧‧‧First Passage

112b‧‧‧second channel

120‧‧‧Piston

120a‧‧‧First compression department

120b‧‧‧Second compression department

120c‧‧‧ Sealing structure

130‧‧‧Oil check valve

140‧‧‧pressure regulator

150‧‧‧ return pipe

210‧‧‧Hydraulic cylinder

212‧‧‧ openings

220‧‧‧Separator

300‧‧‧ oil storage tank

400‧‧‧Piston assembly

1000‧‧‧diaphragm compressor

Claims (8)

A pump oil structure of a diaphragm compressor, the diaphragm compressor having at least two diaphragm compression assemblies, comprising: at least two pairs of sliding sleeves, wherein each of the sliding sleeves has a hollow tube, the hollow tube is connected to the One of the diaphragm compression assemblies; wherein the hollow conduit includes a first passage and a second passage, the first passage having a larger diameter than the second passage, and the second passage connecting the corresponding diaphragm compression assembly; a piston assembly having two pistons interlocking with each other; wherein each piston has a first compression portion and a second compression portion; wherein the diameter of the first compression portion is greater than the second compression portion, and the first compression portion Reciprocatingly moving in the first passage, thereby driving the second compression portion to reciprocate in the second passage, and a sealing structure is disposed between the first compression portion and the first passage; Connected to each of the first passages of the hollow pipe, and between the sealing structure and the second passage for unidirectionally leaving the hydraulic oil body; and two return pipes, one end of each of the oil return pipes is connected to One of the two diaphragm compression assemblies, the other end being connected to an oil discharge check valve corresponding to the other diaphragm compression assembly for receiving the hydraulic oil body; wherein, when the piston moves toward the diaphragm compression assembly, The difference in diameter between the first compression portion and the second compression portion causes a volume effect to drive the hydraulic oil body to exit through the oil discharge check valve; when the piston is away from the diaphragm compression assembly, the first compression portion and the The difference in diameter of the second compression portion causes a volumetric effect, and the hydraulic oil body is driven to replenish through the oil return pipe to the diaphragm compression assembly. The pump oil structure of the diaphragm compressor according to claim 1, further comprising a pressure regulating valve connected to the diaphragm compression assembly for overflowing the hydraulic oil body to a pressure when the pressure exceeds a predetermined pressure Oil storage tank. The pump oil structure of the diaphragm compressor of claim 1, wherein the sealing structure is an oil seal ring. A diaphragm compressor comprising: at least two diaphragm compression assemblies; at least two pairs of sliding sleeves, wherein each of the sliding sleeves respectively has a hollow tube connecting one of the diaphragm compression assemblies; The hollow duct includes a first passage and a second passage, the first passage having a diameter larger than the second passage, and the second passage connecting the corresponding diaphragm compression assembly; and a piston assembly having two interlocking movements a piston; each of the pistons has a first compression portion and a second compression portion; wherein the first compression portion has a larger diameter than the second compression portion, and the first compression portion reciprocates in the first passage, thereby Driving the second compression portion to reciprocate in the second passage, and providing a sealing structure between the first compression portion and the first passage; and two oil discharge check valves respectively connected to the first of the hollow conduits a passage between the sealing structure and the second passage for unidirectionally separating the hydraulic oil body of the corresponding diaphragm compression assembly; and two return oil pipes, one end of each of the oil return pipes being connected to the two diaphragms One of the other ends is connected to an oil discharge check valve corresponding to another diaphragm compression assembly for receiving the hydraulic oil body; wherein, when the piston moves toward the diaphragm compression assembly, the first a difference in diameter between a compression portion and the second compression portion causes a volume effect to drive the hydraulic oil body to exit through the oil discharge check valve; and when the piston is away from the diaphragm compression assembly, the first compression portion and the first portion The difference in diameter of the two compression portions causes a volumetric effect, and the hydraulic oil body is driven to replenish through the oil return pipe to the diaphragm compression assembly. The diaphragm compressor of claim 4, wherein each of the diaphragm compression assemblies comprises: a hydraulic cylinder connected to the second passage of the hollow conduit, and the hydraulic cylinder has an opening; And a diaphragm that closes the opening, and the hydraulic oil body is driven by the reciprocating movement of the piston to bulge or contract outward. The diaphragm compressor of claim 4, wherein each of the sealing structures is an oil seal ring. The diaphragm compressor of claim 5 further comprising an oil reservoir connected to the two hydraulic cylinders. The diaphragm compressor of claim 7, further comprising two pressure regulating valves respectively connected to one of the hydraulic cylinders of the two diaphragm compression assemblies for making the hydraulic oil body when the pressure exceeds a predetermined pressure Overflow to the sump.