Large-flow diaphragm compressor

Abstract

The invention belongs to the technical field of diaphragm compressors, and particularly relates to a high-flow diaphragm compressor. A piston body of the high-flow diaphragm compressor comprises a piston rod, a first piston body and a second piston body. The first piston body can axially reciprocate in the diaphragm head main body, one end of the piston rod extends into the diaphragm head main body and then abuts against the first piston body, and the other end of the piston rod is used for being connected with the crosshead main body; the second piston body is arranged on the piston rod, is positioned in the middle body in a sliding manner, and can axially reciprocate in the middle body of the machine body; the axial sliding length of the second piston body in the middle body is larger than that of the first piston body. A partition plate is detachably arranged at the end, close to one side of the crankcase, of the middle body, and the other end of the piston rod penetrates through the partition plate and then is connected with the crosshead body. The auxiliary double-acting piston compressor is adopted for pre-compressing, supplementing and adjusting the flow of the diaphragm compressor, and then the flow adaptability of diaphragm compression under different working conditions is improved.

Description

Technical Field

[0001] The invention belongs to the technical field of diaphragm compressors, and in particular relates to a large-flow diaphragm compressor. Background Art

[0002] The diaphragm compressor is a positive displacement compressor. Unlike the traditional reciprocating piston compressor that compresses gas directly through the piston, the diaphragm compressor compresses gas by pushing the hydraulic oil through the piston and then driving the diaphragm to reciprocate. The diaphragm divides the compression chamber into an air chamber and an oil chamber. The deformation of the diaphragm is limited by the air side diaphragm head and the oil side diaphragm head. Therefore, the volume change of the air chamber is larger than that of the piston machine, and the suction volume is therefore smaller, resulting in a smaller flow rate. However, it has the advantages of low vibration, low noise, small clearance volume, and smooth operation, so it is widely used.

[0003] The structure of the existing diaphragm compressor is as follows Figure 1 As shown, it includes a diaphragm head assembly 01 (including an air side diaphragm head 01A and an oil side diaphragm head 01B), a piston assembly 02, a crosshead assembly 03, a body assembly 04 (including a middle body 41 and a crankcase 04B), a crankshaft connecting rod assembly 05, and a plunger pump assembly 06. First, the air-side diaphragm head and the oil-side diaphragm head are connected to form a diaphragm head assembly 01 through studs; the metal diaphragm is placed between the air-side diaphragm head and the oil-side diaphragm head, and is compressed by the pre-tightening force of the studs; the middle body 41 and the crankcase 04B are connected to form the fuselage assembly 04 through studs, and then the diaphragm head assembly 01 and the fuselage assembly 04 are connected by threads; the crosshead assembly 03 and the piston assembly 02 and the crankshaft connecting rod assembly 05 are all connected by threads; the crankshaft connecting rod assembly 05 is placed in the crankcase; the crosshead assembly 03 is placed in the slideway of the middle body 41; the plunger pump assembly 06 is attached to the non-flywheel side of the crankshaft, and the hydraulic oil is extracted from the crankcase 04B and replenished into the oil-side diaphragm cavity. The motor drives the crank-connecting rod mechanism, which in turn drives the piston to reciprocate. The piston pushes the hydraulic oil to transmit the reciprocating motion to the metal diaphragm, thereby changing the volume of the air-side diaphragm cavity and compressing the gas. However, the flow rate of the above-mentioned diaphragm compressor is not easy to adjust.

[0004] Application No. 201811362196.3 discloses a diaphragm compressor and a flow control method thereof, and Application No. 201811132705.3 discloses a diaphragm compressor and a flow control method thereof. Both of them realize stepless regulation of the gas flow of the diaphragm compressor when the machine is running by adjusting the oil replenishment timing of the plunger pump, which can solve the problem of insufficient air intake when the existing diaphragm compressor replenishes oil. However, the adjustment range of this improvement is limited. When the air intake is low, the air intake volume is small; there is no efficient flow control device, and the flow adjustment through the valve depends on the state of the intake and exhaust gas, which is often bound to the pressure and cannot achieve autonomous flow adjustment; during the filling process, when the exhaust pressure gradually rises, the flow will also slowly decrease. Summary of the invention

[0005] In order to solve the above problems, the present invention provides a large flow diaphragm compressor, which uses an auxiliary double-acting piston compressor to perform pre-compression, supplement and adjust the flow of the diaphragm compressor, thereby improving the adaptability of the flow of the diaphragm compressor under different working conditions.

[0006] The present invention solves the above technical problems through the following technical solutions.

[0007] The object of the present invention is to provide a large flow diaphragm compressor, comprising a diaphragm head body, a piston body, a body body and a crosshead body arranged in sequence along the axial direction, wherein the body body comprises a middle body and a crankcase connected in sequence along the axial direction, and the piston body comprises a piston rod, a first piston body and a second piston body; The first piston body can axially reciprocate in the membrane head body, one end of the piston rod is inserted into the membrane head body and abuts against the first piston body, and the other end is used to connect to the crosshead body; The second piston body is arranged on the piston rod, and the second piston body is slidably located in the middle body and can axially reciprocate in the middle body; the axial sliding length of the second piston body in the middle body is greater than the axial sliding length of the first piston body; A partition plate is detachably provided at the end of the middle body close to the crankcase, and the other end of the piston rod is connected with the crosshead body after passing through the partition plate.

[0008] Furthermore, in the above-mentioned large-flow diaphragm compressor, a cylinder sleeve is provided in the diaphragm head body, a cylinder hole is provided in the cylinder sleeve, the first piston body can axially reciprocate in the cylinder hole, a first sealing ring is circumferentially provided in the cylinder hole close to the middle body, and one end of the piston rod extends into the first sealing ring and abuts against the first piston body.

[0009] Furthermore, in the above-mentioned large-flow diaphragm compressor, a second sealing ring is circumferentially provided at the contact end between the second piston body and the middle body.

[0010] Furthermore, in the above-mentioned large-flow diaphragm compressor, an oil-gas sealing ring is circumferentially provided between the partition plate and the end of the middle body, and a third sealing ring is circumferentially provided between the partition plate and the piston rod.

[0011] Furthermore, in the above-mentioned large-flow diaphragm compressor, along the axial direction of the main body of the fuselage, the second piston body and the partition plate divide the main body of the fuselage into a first chamber, a second chamber and a third chamber in sequence, wherein the first chamber and the second chamber are not connected to the atmosphere.

[0012] Furthermore, in the above-mentioned large-flow diaphragm compressor, the first chamber of the middle body is provided with a first radial through hole, a second radial through hole, a third radial through hole, a fourth radial through hole, a fifth radial through hole and a sixth radial through hole, wherein the first radial through hole, the second radial through hole and the fifth radial through hole are close to the cylinder sleeve, the third radial through hole, the fourth radial through hole and the sixth radial through hole are close to the partition, the first radial through hole is provided with a first intake valve, the third radial through hole is provided with a second intake valve, the second radial through hole is provided with a first exhaust valve, and the fourth radial through hole is provided with a second exhaust valve.

[0013] Furthermore, in the above-mentioned large-flow diaphragm compressor, the first exhaust valve and the second exhaust valve are both connected in parallel with the intake valve of the diaphragm compressor to exhaust gas, so as to adjust the exhaust pressure and flow rate.

[0014] Furthermore, in the above-mentioned large-flow diaphragm compressor, the fifth radial through hole is connected to the sixth radial through hole through a pipeline, and a stop valve is provided on the pipeline.

[0015] Furthermore, in the above-mentioned large-flow diaphragm compressor, an oil hole is provided inside the piston rod for lubricating the second piston body.

[0016] Compared with the prior art, the present invention has the following beneficial effects: (9) The diaphragm compressor piston body provided by the present invention has a first piston body and a second piston body arranged on the piston rod to construct a double-acting piston compressor, wherein the first piston body can axially reciprocate in the diaphragm head body, and the second piston body is slidably located in the middle body and can axially reciprocate in the middle body. The suction air is pre-compressed through the auxiliary piston compressor structure, thereby realizing a large flow suction of the diaphragm compressor, improving the flow operating range of the compressor, and further improving the flow adaptability of the diaphragm compression under different working conditions.

[0017] (2) The piston body provided by the present invention is an improvement on the original diaphragm compressor piston, that is, it is directly attached to the original mechanism, does not need to be connected in series or parallel with other equipment, reduces the complexity of the equipment, and can be adjusted according to the change in required blood flow. In situations where flow regulation is not required, it can also serve as a piston compressor to compress other gases, thereby improving economic benefits. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a schematic structural diagram of an existing diaphragm compressor of the present invention.

[0019] Figure 2 It is a schematic structural diagram of a large flow diaphragm compressor of the present invention.

[0020] Figure 3 It is a structural schematic diagram of the piston body of the present invention.

[0021] Figure 4It is a three-dimensional schematic diagram of the piston body of the present invention.

[0022] Figure 5 It is a schematic structural diagram of the partition of the present invention.

[0023] Figure 6 It is a three-dimensional schematic diagram of the partition of the present invention.

[0024] Illustration Description: 1. Diaphragm head body, 101. Cylinder sleeve, 102. Air side diaphragm head, 103. Oil side diaphragm head, 2. Piston body, 21. Piston rod, 22. First piston body, 23. Second piston body, 3. Crosshead body, 4. Fuselage body, 41. Middle body, 411. Partition, 4111. First shell, 4112. Second shell, 42. Crankcase, 5. Crankshaft connecting rod body, 6. Plunger pump body, 7. First sealing ring, 8. Second sealing ring, 9. Oil and gas sealing ring, 10. Third sealing ring, 11. Stop valve.

[0025] IA, first chamber, IB, second chamber, IC, third chamber, IIA, first radial through hole, IIB, second radial through hole, IIC, third radial through hole, IID, fourth radial through hole, IIE, fifth radial through hole, IIF, sixth radial through hole.

[0026] 01. Diaphragm head assembly, 01A. Air side diaphragm head 01A, 01B. Oil side diaphragm head, 02. Piston assembly, 03. Crosshead assembly, 04. Body assembly, 05. Crankshaft connecting rod assembly, 06. Plunger pump assembly. DETAILED DESCRIPTION

[0027] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0028] It should be noted that the professional terms used in the present invention are only for the purpose of describing specific embodiments and are not intended to limit the scope of protection of the present invention. Certain words are used in the present invention to refer to specific components. Those skilled in the art should understand that technicians will use different nouns to refer to the same component. The present invention does not distinguish between components by the difference in nouns, but by the difference in the functions of the components. As mentioned throughout the specification and claims, "including" is an open term and should be understood as "including but not limited to".

[0029] A diaphragm compressor is a reciprocating compressor that compresses and transports gas by reciprocating motion of a diaphragm in a cylinder. The diaphragm is clamped by two limiting plates along the periphery to form a cylinder. Common diaphragm compressors use a metal diaphragm and are driven by hydraulic force to reciprocate in the cylinder to achieve gas compression and transportation. The advantage of a diaphragm compressor is that the clearance volume is small, and a high pressure ratio can be achieved. However, due to the limited volume of the diaphragm cavity, the suction volume of the diaphragm compressor under low-pressure intake will be very small, and it cannot adapt to large flow transportation.

[0030] Based on this, in order to solve the problem of small flow rate of diaphragm compressor, such as Figure 2 As shown, the present invention designs a large flow diaphragm compressor, by adding a piston to the original piston rod to construct a double-acting piston compressor, to pre-compress the suction air and increase the suction volume of the diaphragm compressor. The large flow diaphragm compressor includes a diaphragm head body 1, a piston body 2, a body body 4 and a crosshead body 3 arranged in sequence along the axial direction, wherein the body body 4 includes a middle body 41 and a crankcase 42 connected in sequence in the axial direction, as shown in FIG. Figure 2 to Figure 4 As shown, the piston body 2 includes a piston rod 21, a first piston body 22 and a second piston body 23; wherein the first piston body 22 can axially reciprocate in the diaphragm head body 1, one end of the piston rod 21 extends into the diaphragm head body 1 and abuts against the first piston body 22, and the other end is used to connect the crosshead body 3; the second piston body 23 is arranged on the piston rod 21, and the second piston body 23 is slidably located in the middle body 41 and can axially reciprocate in the middle body 41; the axial sliding length of the second piston body 23 in the middle body 41 is greater than the axial sliding length of the first piston body 22; the end of the middle body 41 close to the crankcase 42 is detachably provided with a partition 411, and the other end of the piston rod 21 is connected to the crosshead body 3 after passing through the partition 411.

[0031] It should be noted that the large-flow diaphragm compressor provided by the present invention comprises a diaphragm head body 1, a fuselage body 4, and a crosshead body 3 which are sequentially arranged along the axial direction, and also comprises a crankshaft connecting rod body 5, which is rotatably arranged in a crankcase 42 of the fuselage body 4, and the crankshaft connecting rod body 5 is rotatably connected to the crosshead body 3, and is used to drive the crosshead body 3 to reciprocate, and the crankshaft connecting rod body 5 is connected to a plunger pump body 6, and the plunger pump body 6 is used to drive the crankshaft connecting rod body 5 to move, thereby driving the piston body 2 to reciprocate, and the diaphragm head body 1, the fuselage body 4, the crosshead body 3, the crankshaft connecting rod body 5 and the plunger pump body 6 mentioned above are all structures of existing diaphragm compressors, wherein the diaphragm head body 1 comprises an air side The diaphragm head 102 and the oil side diaphragm head 103, the air side diaphragm head 102 and the oil side diaphragm head 103 are connected to form a diaphragm head body 1 through studs, and the metal diaphragm is placed between the air side diaphragm head 102 and the oil side diaphragm head 103, and is compressed by the pre-tightening force of the studs; the fuselage body 4 includes a middle body 41 and a crankcase 42, the middle body 41 and the crankcase 42 are connected to form a fuselage body 4 through studs, and the diaphragm head body 1 is connected to the fuselage body 4 through threads; the crosshead body 3 and the piston body 2 and the crankshaft connecting rod body 5 are all connected through threads, and the crankshaft connecting rod body 5 is placed in the crankcase; the crosshead assembly 03 is placed in the slideway of the middle body 41; a plunger pump body 6 is attached to the non-flywheel side of the crankshaft to draw hydraulic oil from the crankcase 42 and replenish it into the oil side diaphragm cavity. On the basis of the structure of the above-mentioned existing diaphragm compressor, the present invention redesigns a piston body 2, and sets a first piston body 22 and a second piston body 23 on the piston rod 21 to construct a double-acting piston compressor. The second piston body 23 and the internal part of the journal of the middle body 41 cooperate with each other. At the bottom point of the movement of the second piston body 23, that is, at the farthest distance from the diaphragm head, a partition 411 parallel to the second piston body 23 and fixed to the fuselage body is installed. The partition 411 is connected to the middle body 41 by bolts to increase the oil and gas seal. The axial sliding length of the second piston body 23 in the middle body 41 is greater than that of the first piston body 23. The axial sliding length of the plug body 22, that is, the axial sliding length d of the second piston body 23 in the middle body 41 is greater than the stroke S of the first piston body 22, thereby preventing the second piston body 23 from hitting the cylinder. The first piston body 21 can axially reciprocate in the membrane head body 1, and the second piston body 23 slides in the middle body 41 and can axially reciprocate in the middle body 41, thereby constructing an auxiliary piston compressor structure. Through the auxiliary piston compressor structure, the suction air is pre-compressed, thereby realizing large-flow suction of the diaphragm compressor, improving the flow working range of the compressor, and thereby improving the adaptability of the diaphragm compression to the flow under different working conditions.

[0032] To ensure convenient loading and unloading of partitions, Figure 2As shown, the middle body 41 includes a first shell 4111 that cooperates with the crankcase 42, and a second shell 4112 that cooperates with the oil side membrane head 1001 and the partition plate 411. The first shell 4111 and the second shell 4112 are connected by bolts.

[0033] In a specific embodiment, a cylinder sleeve 101 is provided in the membrane head body 1, and a cylinder hole is provided in the cylinder sleeve 101. The first piston body 22 can axially reciprocate in the cylinder hole. A first sealing ring 7 is circumferentially provided in the cylinder hole close to the middle body 41. One end of the piston rod extends into the first sealing ring 7 and abuts against the first piston body.

[0034] In a specific embodiment, a second sealing ring 8 is provided circumferentially between the contact ends of the second piston body 23 and the middle body 41. A second machined sealing groove is provided circumferentially between the contact ends of the second piston body 23 and the middle body 41 for installing the second sealing ring.

[0035] It should be noted that when the first piston body 21 performs axial reciprocating motion in the cylinder hole, the first piston body 21 pushes the hydraulic oil, which is a crude oil side seal, and a first sealing ring 7 is circumferentially provided in the cylinder hole near the middle body 41, and a second sealing ring 8 is circumferentially provided at the contact end of the second piston body 23 and the middle body 41, and a sealing gas is formed by the first sealing ring 7 and the second sealing ring 8, wherein the piston body 23 and the middle body 41 are matched through a first gap, and the sealing is increased by the second sealing ring 8.

[0036] In a specific embodiment, an oil and gas sealing ring 9 is circumferentially provided between the partition 411 and the end of the middle body 41, and a third sealing ring 10 is circumferentially provided between the partition 411 and the piston rod. The partition 411 is an annular partition, and a center hole is provided in the center of the annular partition. The other end of the piston rod 21 passes through the center hole and is connected to the crosshead body 3. The center hole and the piston rod 21 are matched through a second gap. The connection surface between the partition 411 and the middle body 41 is provided with a third machined sealing groove for installing the oil and gas sealing ring 9. The oil and gas sealing ring 9 is used to perform oil and gas sealing to prevent the gas in the first chamber IA and the second chamber IB from leaking to both sides, such as Figure 5-6 As shown, the partition plate 411 is fixed to the end of the middle body 41 by bolts for easy disassembly.

[0037] In a specific embodiment, along the axial direction of the fuselage body 4, the second piston body 23 and the partition plate sequentially separate the fuselage body 4 into the first chamber IA, the second chamber IB and the third chamber IC, wherein the first chamber IA and the second chamber IB are not connected to the atmosphere. The places where the first chamber IA and the second chamber IB are connected to the atmosphere are completely sealed, and a second piston body 23 is added to the piston rod 21 by utilizing the reciprocating motion of the diaphragm compressor itself. The second piston body 23 and the partition plate 411 sequentially separate the fuselage body 4 into two working chambers, the first chamber IA and the second chamber IB, thereby forming a double-acting piston compressor system to pre-compress, supplement and adjust the flow of the diaphragm compressor.

[0038] In a specific embodiment, the first chamber IA of the middle body 41 is provided with a first radial through hole IIA, a second radial through hole IIB, a third radial through hole IIC, a fourth radial through hole IID, a fifth radial through hole IIE and a sixth radial through hole IIF, wherein the first radial through hole IIA, the second radial through hole IIB and the fifth radial through hole IIE are close to the cylinder sleeve 101, the third radial through hole IIC, the fourth radial through hole IID and the sixth radial through hole IIF are close to the partition 411, the first radial through hole IIA is provided with a first intake valve, the third radial through hole IIC is provided with a second intake valve, the second radial through hole IIB is provided with a first exhaust valve, and the fourth radial through hole IID is provided with a second exhaust valve. When the first piston body 21 moves toward the diaphragm head, the first intake valve and the first exhaust valve are located on the inner wall of the first chamber IA, and the second intake valve and the second exhaust valve are located on the inner wall of the second chamber IB. At this time, the first intake valve is closed, the first exhaust valve is opened, the second intake valve is opened, and the second exhaust valve is closed. When the first piston body 21 moves toward the fuselage, the first intake valve and the first exhaust valve are located on the inner wall of the first chamber IA, and the second intake valve and the second exhaust valve are located on the inner wall of the second chamber IB. At this time, the first intake valve is opened, the first exhaust valve is closed, the second intake valve is closed, and the second exhaust valve is opened. The intake air is pre-compressed through the auxiliary piston compressor structure, thereby realizing large-flow intake of the diaphragm compressor, improving the flow operating range of the compressor, and thereby improving the flow adaptability of the diaphragm compression under different working conditions.

[0039] In a specific embodiment, the first exhaust valve and the second exhaust valve are both connected in parallel with the intake valve of the diaphragm compressor to exhaust gas, so as to adjust the exhaust pressure and flow rate.

[0040] In a specific embodiment, the fifth radial through hole IIE is connected to the sixth radial through hole IIF through a pipeline, and a stop valve 11 is provided on the pipeline. The pressure difference between the first chamber IA and the second chamber IB is adjusted by the opening of the stop valve 11, and then the clearance volume of the two is increased in disguise to adjust the flow rate. At this time, the suction volume of the diaphragm compressor is reduced. When the piston keeps reciprocating, the first chamber IA and the second chamber IB are compressed and exhausted alternately, and the exhaust pressure and flow rate can be adjusted by the stop valve 11. The exhausted gas is connected to the diaphragm compressor suction valve to increase the suction flow rate of the compressor.

[0041] In a specific embodiment, an oil hole is provided inside the piston rod for lubricating the second piston body 23. In order to avoid dry friction of the piston 02B, an oil hole is provided inside the piston rod to lubricate the second piston body 23.

[0042] In summary, the present invention provides a large flow diaphragm compressor, which divides the fuselage into three chambers, namely, the first chamber IA, the second chamber IB and the third chamber IC, on the left, middle and right sides, through the second piston body and the partition. An air seal is added near the end of the first chamber IA of the second piston body 23, that is, the original oil seal is changed to an oil and gas double-side seal, and the total axial length d of the first chamber IA and the second chamber IB is determined according to the piston stroke S (so that d is slightly larger than S to avoid collision with the cylinder). When the piston moves toward the diaphragm head, the first suction valve is closed, the first exhaust valve is opened, the second suction valve is opened, and the second exhaust valve is closed; when the piston moves toward the fuselage, the first suction valve is opened, the first exhaust valve is closed, the second suction valve is closed, and the second exhaust valve is opened. When the piston keeps reciprocating, the first chamber IA and the second chamber IB are alternately compressed and exhausted. At this time, the clearance can be changed by the relationship between the stroke S and the total length d, or a circuit can be added to adjust the exhaust pressure and flow, and the exhausted gas is connected to the diaphragm compressor suction valve to increase the suction flow of the compressor.

[0043] It should be noted that when the present invention involves a numerical range, it should be understood that the two endpoints of each numerical range and any value between the two endpoints can be selected. Since the steps and methods used are the same as those in the embodiments, in order to avoid redundancy, the present invention describes a preferred embodiment. Although the preferred embodiments of the present invention have been described, those skilled in the art may make additional changes and modifications to these embodiments once they know the basic creative concept. Therefore, the attached claims are intended to be interpreted as including the preferred embodiments and all changes and modifications that fall within the scope of the present invention.

[0044] Obviously, those skilled in the art can make various changes and modifications to the present invention without departing from the spirit and scope of the present invention. Thus, if these modifications and variations of the present invention fall within the scope of the claims of the present invention and their equivalents, the present invention is also intended to include these modifications and variations.

Claims

1. A large flow diaphragm compressor, comprising a diaphragm head body (1), a piston body (2), a body body (4) and a crosshead body (3) arranged in sequence along the axial direction, wherein: The fuselage body (4) comprises a middle body (41) and a crankcase (42) which are axially connected in sequence, and is characterized in that the piston body (2) comprises a piston rod (21), a first piston body (22) and a second piston body (23); The first piston body (22) is capable of axially reciprocating movement in the diaphragm head body (1); one end of the piston rod (21) extends into the diaphragm head body (1) and abuts against the first piston body (22); the other end is used to connect to the crosshead body (3); The second piston body (23) is arranged on the piston rod (21), and the second piston body (23) is slidably located in the middle body (41) and is capable of axially reciprocating movement in the middle body (41); the axial sliding length of the second piston body (23) in the middle body (41) is greater than the axial sliding length of the first piston body (22); A partition plate (411) is detachably provided at the end of the middle body (41) near the crankcase (42), and the other end of the piston rod (21) passes through the partition plate (411) and is connected to the crosshead body (3).

2. The large flow diaphragm compressor according to claim 1, characterized in that: A cylinder sleeve (101) is provided in the diaphragm head body (1), a cylinder hole is provided in the cylinder sleeve (101), the first piston body (22) is capable of axially reciprocating in the cylinder hole, a first sealing ring (7) is circumferentially provided in the cylinder hole close to the middle body (41), and one end of the piston rod (21) extends into the first sealing ring (7) and abuts against the first piston body (22).

3. The large flow diaphragm compressor according to claim 1, characterized in that: A second sealing ring (8) is circumferentially provided at the contact end of the second piston body (23) and the middle body (41).

4. The large flow diaphragm compressor according to claim 1, characterized in that: An oil and gas sealing ring (9) is circumferentially arranged between the partition plate (411) and the end of the middle body (41), and a third sealing ring (10) is circumferentially arranged between the partition plate (411) and the piston rod (21).

5. The large flow diaphragm compressor according to claim 1, characterized in that: Along the axial direction of the fuselage main body (4), the second piston body (23) and the partition plate divide the fuselage main body (4) into a first chamber (IA), a second chamber (IB) and a third chamber (IC) in sequence, wherein the first chamber (IA) and the second chamber (IB) are not connected to the atmosphere.

6. The large flow diaphragm compressor according to claim 5, characterized in that: A first radial through hole (IIA), a second radial through hole (IIB), a third radial through hole (IIC), a fourth radial through hole (IID), a fifth radial through hole (IIE) and a sixth radial through hole (IIF) are provided on the first chamber (IA) of the middle body (41), wherein the first radial through hole (IIA), the second radial through hole (IIB) and the fifth radial through hole (IIE) are close to the cylinder sleeve (101), the third radial through hole (IIC), the fourth radial through hole (IID) and the sixth radial through hole (IIF) are close to the partition (411), the first radial through hole (IIA) is provided with a first intake valve, the third radial through hole (IIC) is provided with a second intake valve, the second radial through hole (IIB) is provided with a first exhaust valve, and the fourth radial through hole (IID) is provided with a second exhaust valve.

7. The large flow diaphragm compressor according to claim 6, characterized in that: The first exhaust valve and the second exhaust valve are both connected in parallel with the intake valve of the diaphragm compressor to exhaust gas, so as to adjust the exhaust pressure and flow rate.

8. The large flow diaphragm compressor according to claim 6, characterized in that: The fifth radial through hole (IIE) is connected to the sixth radial through hole (IIF) via a pipeline, and a stop valve (11) is provided on the pipeline.

9. The large flow diaphragm compressor according to claim 1, characterized in that: An oil hole is provided inside the piston rod (21) for lubricating the second piston body (23).

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