Connecting body structure of stepless air flow regulation actuator of reciprocating compressor

Abstract

The invention discloses a connector structure of a stepless air flow regulation actuator of a reciprocating compressor, which relates to the technical field of reciprocating compressors and comprises an ejector rod, a shell, a connecting piece and a sealing assembly. The ejector rod is used for transmitting power provided by the driving structure to the unloader, and the shell is arranged on the outer side of the ejector rod in a sleeving mode. The connecting piece comprises a flange part and a sleeve part. The first side of the flange part is used for connecting the second end of the shell, and the second side of the flange part is used for connecting a shell of the driving structure. The sleeve part is located between the ejector rod and the shell and provided with a second oil hole, and the second oil hole is in butt joint with the first oil hole. The sealing assembly comprises a first end face sealing ring, a second end face sealing ring, a first sealing ring and an oil leakage connector. The oil leakage connector is connected with the first oil hole and used for recycling hydraulic oil when the driving structure is a hydraulic cylinder. Compared with the prior art, the connector structure can adapt to two driving modes of hydraulic force and electromagnetic force, and has better universality.

Description

Technical Field

[0001] The invention relates to the technical field of reciprocating compressors, and in particular to a connecting body structure of a stepless gas volume regulating actuator of a reciprocating compressor. Background Art

[0002] As a key dynamic equipment in process industries such as oil refining, chemical industry, and fertilizer industry, the reciprocating compressor system transports high-pressure raw gas medium to the production process. It is a key node in the material flow of industrial production. Its safe, stable, and reliable operation is a long-term need of enterprises.

[0003] Reciprocating compressors change the volume of the working chamber between the piston and the cylinder through the periodic movement of the piston, thereby controlling the gas pressure in the working chamber; but when the initial design of the process does not match the market demand, the exhaust volume of the unit needs to be dynamically adjusted to meet production requirements. At present, the adjustment method that can meet both energy conservation and production gas supply and demand is the top-opening intake valve adjustment. Installing an electro-hydraulic servo actuator or electromagnetic actuator on the intake valve can quickly and accurately control the flow and pressure of the unit; compared with other adjustment methods, it has the advantages of low engineering implementation difficulty, wide load adjustment range, and the most outstanding energy-saving effect.

[0004] The regulating system of the top-opening air inlet valve has been publicized both at home and abroad. The actuator is driven by hydraulic pressure or electromagnetic force. According to the different driving methods, actuators in the prior art are generally divided into two categories, and universal structural design is not considered. If different actuators are installed on the same type of unit, it is difficult to achieve component interchangeability, which brings great difficulties to on-site installation, maintenance and spare parts management. Summary of the invention

[0005] The purpose of the present invention is to provide a reciprocating compressor stepless gas volume regulation actuator connecting body structure to solve the problems existing in the above-mentioned related technologies and adapt to two driving modes: hydraulic pressure and electromagnetic force.

[0006] To achieve the above object, the present invention provides the following solutions:

[0007] The present invention discloses a reciprocating compressor stepless gas volume regulation actuator connecting body structure, comprising:

[0008] A push rod, wherein a first end of the push rod is used to connect to a top plate of the unloader, and a second end of the push rod is used to connect to a driving end of a driving structure;

[0009] A housing, wherein the housing is sleeved on the outside of the push rod and a gap is left between the housing and the push rod; the housing is provided with a first oil hole, and the two ends of the first oil hole are respectively located on the inner side and the outer side of the housing; the first end of the housing is used to connect the valve cover of the compressor;

[0010] A connecting piece, the connecting piece comprises a flange portion and a sleeve portion; the first side of the flange portion is used to connect to the second end of the shell, the second side of the flange portion is used to connect to the shell of the driving structure, and is in sealing contact with the shell; the sleeve portion is connected to the side of the flange portion away from the driving structure, the sleeve portion is located between the push rod and the shell, and a gap is left between the push rod; the sleeve portion is provided with a second oil hole, the two ends of the second oil hole are respectively located on the inner side and the outer side of the sleeve portion; the second oil hole is butted against the first oil hole;

[0011] A sealing assembly, the sealing assembly comprising a first end face sealing ring, a second end face sealing ring, a first sealing ring and an oil leakage joint; the first end face sealing ring is used to seal the gap between the first side of the flange portion and the shell, and the second end face sealing ring is used to seal the gap between the valve cover and the shell; the first sealing ring is located between the push rod and the shell, and is located on the side of the sleeve portion away from the drive structure, the inner side surface of the first sealing ring is in sealing contact with the push rod, and the outer side surface of the first sealing ring is in sealing contact with the inner side surface of the shell to seal the gap between the push rod and the shell; the oil leakage joint is connected to the first oil hole, and is used to recover hydraulic oil when the drive structure is a hydraulic cylinder.

[0012] Preferably, the sealing assembly also includes an air guide ring and an air leakage joint; the air guide ring is located between the push rod and the shell, and is located on the side of the first sealing ring away from the driving structure, the air guide ring is provided with a first air hole, and the two ends of the first air hole are respectively located on the inner side and outer side of the air guide ring; the shell is provided with a second air hole, and the two ends of the second air hole are respectively located on the inner side and outer side of the shell, and the second air hole is connected to the first air hole; the air leakage joint is connected to the second air hole for recovering gas leaked from the compressor.

[0013] Preferably, the sealing assembly also includes a second sealing ring; the second sealing ring is located between the push rod and the shell, and is located on the side of the air guide ring away from the drive structure, the inner side surface of the second sealing ring is in sealing contact with the push rod, and the outer side surface of the second sealing ring is in sealing contact with the inner side surface of the shell to seal the gap between the push rod and the shell, so as to reduce the amount of gas leaked from the compressor to the air guide ring.

[0014] Preferably, the housing is provided with an inner flange, the inner flange is located on a side of the second sealing ring away from the driving structure, and is used to limit the circumferential position of the second sealing ring; the push rod passes through the inner flange.

[0015] Preferably, the second sealing ring includes a second ring block, an inner sealing ring of the second ring block and an outer sealing ring of the second ring block; the second ring block is located between the push rod and the shell, the inner sealing ring of the second ring block is embedded in the inner side surface of the second ring block, and is used for sealing contact with the push rod; the outer sealing ring of the second ring block is embedded in the outer side surface of the second ring block, and is used for sealing contact with the inner side surface of the shell.

[0016] Preferably, an inner ring groove is provided on the inner side surface of the air guide ring, and an outer ring groove is provided on the outer side surface of the air guide ring; one end of the first air hole is connected to the inner ring groove, and the other end of the first air hole is connected to the outer ring groove.

[0017] Preferably, the first sealing ring includes a first ring block, an inner sealing ring of the first ring block and an outer sealing ring of the first ring block; the first ring block is located between the push rod and the shell, the inner sealing ring of the first ring block is embedded in the inner side surface of the first ring block, and is used for sealing contact with the push rod; the outer sealing ring of the first ring block is embedded in the outer side surface of the first ring block, and is used for sealing contact with the inner side surface of the shell.

[0018] Preferably, the second oil hole is arranged obliquely relative to the sleeve portion; the second oil hole is located at one end of the inner side surface of the sleeve portion, which is closer to the driving structure than the second oil hole is located at one end of the outer side surface of the sleeve portion.

[0019] Preferably, when selecting the return spring of the unloader, the following requirements must be met:

[0020]

[0021] When selecting the drive structure, the following requirements must be met:

[0022]

[0023] in:

[0024] p cy : The air pressure in the compressor;

[0025] p0: standard atmospheric pressure;

[0026] p s : The air pressure in the suction chamber of the compressor;

[0027] β: pressure difference coefficient on both sides of the valve plate of the unloader;

[0028] A sv : The area of ​​the valve plate;

[0029] A l : the cross-sectional area of ​​the ejector pin, d1 is the diameter of the section of the push rod close to the driving structure, and the diameter of the section of the push rod away from the driving structure is d2=1.5d1;

[0030] f: the friction force on the ejector rod;

[0031] g: acceleration due to gravity;

[0032] L: the stroke of the unloader;

[0033] α: The installation angle of the unloader, which refers to the angle between the center line of the unloader and the vertical line of the ground;

[0034] m: the sum of the masses of the ejector rod, the outer shell of the unloader, the top plate of the unloader, the pressure fork of the unloader, and the pressure cover of the unloader;

[0035] x1: pre-compression amount of the return spring;

[0036] F g2 : The gas force on the valve plate, F g2 =β(p cy -p s )A sv ;

[0037] k: the stiffness of the return spring;

[0038] x: compression amount of the return spring;

[0039] F′: the driving force exerted by the driving structure on the ejector rod during the withdrawal of the ejector rod;

[0040] F: The driving force of the driving structure on the ejector during the ejection process of the ejector.

[0041] Preferably, when selecting the ejector rod, the diameter of the ejector rod is determined by the following iterative calculation method:

[0042] Initially, substitute d1=10mm into the formula Calculate the driving force in the ejection state;

[0043] If F≤800N, then d1=10mm, and the diameter of the push rod is determined;

[0044] If F>800N, the diameter of the push rod needs to be increased, and the diameter of the push rod is increased to d1=12mm;

[0045] Substitute d1=12mm into formula (11) and perform iterative calculation to calculate the driving force F in the ejection state;

[0046] If 800N≤F≤1600N, then d1=12mm, and the diameter of the ejector pin is determined;

[0047] If F>1600N, the diameter of the push rod needs to be increased, d1=14mm, the strength is sufficient to meet the use, the iterative calculation is completed, and the diameter of the push rod is determined.

[0048] Compared with the related art, the present invention has achieved the following technical effects:

[0049] The connector of the present invention has a flange portion, which is used to connect to the outside of the driving structure. The driving structure here can be either a hydraulic cylinder or an electromagnetic driving structure, so that the connector can adapt to both hydraulic pressure and electromagnetic force driving modes, thereby improving overall versatility.

[0050] In a preferred embodiment of the present invention, the second side of the flange portion is brought into sealing contact with the outer shell of the driving structure, and the gap between the first side of the flange portion and the shell is sealed by a first end face sealing ring, thereby guiding the leaked hydraulic oil along the gap between the sleeve portion and the push rod to the second oil hole, and the hydraulic oil reaches the leaking joint through the second oil hole and the first oil hole, thereby realizing the recovery of the hydraulic oil, thereby keeping it clean and reducing the waste of hydraulic oil.

[0051] In the preferred embodiment of the present invention, the sealing assembly further comprises an air guide ring and an air leakage joint. Since the second end face sealing ring seals the gap between the valve cover and the housing, the gas leaking from the air suction chamber flows along the push rod to the air guide ring, and then reaches the air leakage joint through the first air hole and the second air hole, thereby realizing the recovery of the leaked gas.

[0052] In a preferred embodiment of the present invention, the sealing assembly further comprises a second sealing ring. The second sealing ring is located between the push rod and the housing, and is located on the side of the air guide ring away from the driving structure. The inner side of the second sealing ring is in sealing contact with the push rod, and the outer side of the second sealing ring is in sealing contact with the inner side of the housing to seal the gap between the push rod and the housing, so as to reduce the amount of gas leaked from the compressor to the air guide ring. The second sealing ring can improve the sealing performance, so that the leaked gas requires a higher air pressure to reach the air guide ring, thereby blocking the airflow to a certain extent and reducing gas leakage.

[0053] In the preferred embodiment of the present invention, a specific calculation method related to the selection of the return spring and the ejector rod is provided, so that the staff can quickly and accurately select the appropriate components for use, improve work efficiency, and ensure the safe operation of the product. BRIEF DESCRIPTION OF THE DRAWINGS

[0054] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or related technologies, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0055] Figure 1 It is a schematic diagram of the connecting body structure of the stepless gas volume regulation actuator of the reciprocating compressor according to an embodiment of the present invention;

[0056] Figure 2 for Figure 1 Assembly diagram of the middle structure, driving structure, unloader and compressor;

[0057] Figure 3 A schematic diagram of force analysis of a connecting body structure of a stepless gas volume regulation actuator for a reciprocating compressor according to an embodiment of the present invention;

[0058] Figure 4 It is a schematic diagram comparing the compression amount of the return spring and the corresponding spring force under different working conditions.

[0059] In the figure: 1-valve plate; 2-valve seat; 3-pressure fork; 4-buffer culvert; 5-outer shell; 6-top plate; 7-valve cover seal ring; 8-valve cover; 9-second end face seal ring; 10-second ring block outer seal ring B; 11-leakage joint; 12-air guide ring; 13-first ring block; 14-first ring block outer seal ring A; 15-leakage joint; 16-connector; 17-first end face seal ring; 18-driving end; 19-driving Structure; 20- ejector rod; 21- first ring block inner seal ring A; 22- first ring block inner seal ring B; 23- first ring block outer seal ring B; 24- housing; 25- second ring block outer seal ring A; 26- first ring block inner seal ring A; 27- second ring block; 28- second ring block inner seal ring B; 29- gland; 30- return spring; 31- suction chamber housing; 32- compressor cylinder wall; 33- noise reduction gasket; DETAILED DESCRIPTION

[0060] 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.

[0061] The purpose of the present invention is to provide a reciprocating compressor stepless gas volume regulation actuator connecting body structure to solve the problems existing in the above-mentioned related technologies and adapt to two driving modes: hydraulic pressure and electromagnetic force.

[0062] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0063] Reference Figure 1 to Figure 4The present embodiment provides a reciprocating compressor stepless gas volume regulation actuator connecting body structure (hereinafter referred to as the connecting body), including a push rod 20, a shell 24, a connecting piece 16 and a sealing assembly.

[0064] The first end of the push rod 20 is used to connect to the top plate 6 of the unloader, and the second end of the push rod 20 is used to connect to the driving end 18 of the driving structure 19. The housing 24 is sleeved on the outside of the push rod 20, and a gap is left between the push rod 20. The housing 24 is provided with a first oil hole, and the two ends of the first oil hole are respectively located on the inner side and the outer side of the housing 24. The first end of the housing 24 is used to connect to the valve cover 8 of the compressor. The connecting member 16 includes a flange portion and a sleeve portion. The first side of the flange portion is used to connect to the second end of the housing 24, and the second side of the flange portion is used to connect to the outer shell of the driving structure 19, and is in sealing contact with the outer shell of the driving structure 19. The sleeve portion connects the side of the flange portion away from the driving structure 19, and the sleeve portion is located between the push rod 20 and the housing 24, and a gap is left between the push rod 20. The sleeve portion is provided with a second oil hole, and the two ends of the second oil hole are respectively located on the inner side and the outer side of the sleeve portion. The second oil hole docks with the first oil hole. The sealing assembly includes a first end face sealing ring 17, a second end face sealing ring 9, a first sealing ring and an oil leakage joint 15. The first end face sealing ring 17 is used to seal the gap between the first side of the flange part and the housing 24, and the second end face sealing ring 9 is used to seal the gap between the valve cover 8 and the housing 24. The first sealing ring is located between the push rod 20 and the housing 24, and is located on the side of the sleeve part away from the driving structure 19. The inner side of the first sealing ring is in sealing contact with the push rod 20, and the outer side of the first sealing ring is in sealing contact with the inner side of the housing 24 to seal the gap between the push rod 20 and the housing 24. The oil leakage joint 15 is connected to the first oil hole, and is used to recover hydraulic oil when the driving structure 19 is a hydraulic cylinder.

[0065] The connector works as follows:

[0066] The driving structure 19 pushes out and withdraws the push rod 20 during operation, and transmits power to the unloader located in the suction chamber of the compressor through the push rod 20, thereby controlling the movement of the valve plate 1 of the unloader to realize the opening and closing of the suction chamber of the compressor.

[0067] The connector 16 has a flange portion, which is used to connect to the outer side of the drive structure 19. The drive structure 19 here can be either a hydraulic cylinder or an electromagnetic drive structure, so that the connector can adapt to both hydraulic and electromagnetic drive modes. A stop structure can be provided on the second side of the flange portion to align with the housing of the drive structure 19.

[0068] When the driving structure 19 is a hydraulic cylinder, there may be a problem of hydraulic oil leakage in the hydraulic cylinder. In order to solve this problem, this embodiment makes the second side of the flange part seal contact with the shell of the driving structure 19, and seals the gap between the first side of the flange part and the housing 24 through the first end face sealing ring 17, so that the leaked hydraulic oil is guided to the second oil hole along the gap between the sleeve part and the push rod 20, and the hydraulic oil reaches the leaking oil joint 15 through the second oil hole and the first oil hole, so as to realize the recovery of the hydraulic oil, thereby keeping it clean and reducing the waste of hydraulic oil.

[0069] The gas in the suction chamber may leak along the position of the push rod 20. The gas pressure is relatively high and may easily cause danger after leakage. As a possible example, in this embodiment, the sealing assembly also includes an air guide ring 12 and a leakage joint 11. The air guide ring 12 is located between the push rod 20 and the shell 24, and is located on the side of the first sealing ring away from the drive structure 19. The air guide ring 12 is provided with a first air hole, and the two ends of the first air hole are respectively located on the inner side and the outer side of the air guide ring 12. The shell 24 is provided with a second air hole, and the two ends of the second air hole are respectively located on the inner side and the outer side of the shell 24, and the second air hole is connected to the first air hole. The leakage joint 11 is connected to the second air hole for recovering gas leaked from the compressor.

[0070] Since the second end face sealing ring 9 seals the gap between the valve cover 8 and the housing 24, the gas leaking from the air intake chamber flows along the push rod 20 to the air guide ring 12, and then reaches the leakage joint 11 through the first air hole and the second air hole, thereby realizing the recovery of the leaked gas.

[0071] In order to reduce the amount of gas leaked from the suction chamber, as a possible example, in this embodiment, the sealing assembly further includes a second sealing ring. The second sealing ring is located between the push rod 20 and the shell 24, and is located on the side of the air guide ring 12 away from the drive structure 19. The inner side of the second sealing ring is in sealing contact with the push rod 20, and the outer side of the second sealing ring is in sealing contact with the inner side of the shell 24, so as to seal the gap between the push rod 20 and the shell 24, so as to reduce the amount of gas leaked from the compressor to the air guide ring 12.

[0072] The second sealing ring can improve the sealing performance, so that the leaked gas needs a higher air pressure to reach the air guide ring 12, thereby blocking the airflow to a certain extent and reducing gas leakage.

[0073] For the first sealing ring, the air guide ring 12 and the second sealing ring between the push rod 20 and the housing 24, their axial positioning reference can be provided by the housing 24, or by a positioning member fixed to the housing 24. As a possible example, in this embodiment, the housing 24 is provided with an inner flange, which is located on the side of the second sealing ring away from the driving structure 19, and is used to limit the circumferential position of the second sealing ring. The push rod 20 passes through the inner flange.

[0074] The inner flange limits the second sealing ring on the side away from the drive structure 19, and the sleeve portion limits the first sealing ring on the side close to the drive structure 19, thereby clamping the first sealing ring, the air guide ring 12 and the second sealing ring between the inner flange and the sleeve portion.

[0075] There are many specific forms of the second sealing ring, as long as the above-mentioned sealing purpose can be achieved. As a possible example, in this embodiment, the second sealing ring includes a second ring block 27, an inner sealing ring of the second ring block, and an outer sealing ring of the second ring block. The second ring block 27 is located between the push rod 20 and the housing 24, and the inner sealing ring of the second ring block is embedded in the inner side surface of the second ring block 27 for sealing contact with the push rod 20. The outer sealing ring of the second ring block is embedded in the outer side surface of the second ring block 27 for sealing contact with the inner side surface of the housing 24.

[0076] Exemplarily, the second ring block inner seal ring includes a second ring block inner seal ring A26 and a second ring block inner seal ring B28, which are separated by a certain distance. The second ring block outer seal ring includes a second ring block outer seal ring A25 and a second ring block outer seal ring B10, which are separated by a certain distance. The second ring block inner seal ring A26 and the second ring block outer seal ring A25 are located at one end of the second ring block 27 close to the drive structure 19, and the second ring block inner seal ring B28 and the second ring block outer seal ring B10 are located at one end of the second ring block 27 away from the drive structure 19.

[0077] In order to improve the efficiency of the leakage gas flow, as a possible example, in this embodiment, an inner ring groove is provided on the inner side of the air guide ring 12, and an outer ring groove is provided on the outer side of the air guide ring 12. One end of the first air hole is connected to the inner ring groove, and the other end of the first air hole is connected to the outer ring groove. The leakage joint 11 can collect the gas in the entire circumferential direction at the same time through the outer ring groove.

[0078] Similarly, an outer annular groove may also be provided at the position where one end of the first oil hole is located on the outer side surface of the housing 24, so that the oil leakage joint 15 can collect the hydraulic oil in the entire circumferential direction at the same time.

[0079] There are many specific forms of the first sealing ring, as long as the above-mentioned sealing purpose can be achieved. As a possible example, in this embodiment, the first sealing ring includes a first ring block 13, an inner sealing ring of the first ring block, and an outer sealing ring of the first ring block. The first ring block 13 is located between the push rod 20 and the housing 24, and the inner sealing ring of the first ring block is embedded in the inner side surface of the first ring block 13, and is used for sealing contact with the push rod 20. The outer sealing ring of the first ring block is embedded in the outer side surface of the first ring block 13, and is used for sealing contact with the inner side surface of the housing 24.

[0080] Exemplarily, the first ring block inner seal ring includes a first ring block inner seal ring A21 and a first ring block inner seal ring B22, which are separated by a certain distance. The first ring block outer seal ring includes a first ring block outer seal ring A14 and a first ring block outer seal ring B23, which are separated by a certain distance. The first ring block inner seal ring A21 and the first ring block outer seal ring A14 are located at one end of the first ring block 13 close to the drive structure 19, and the first ring block inner seal ring B22 and the first ring block outer seal ring B23 are located at one end of the first ring block 13 away from the drive structure 19.

[0081] Exemplarily, the lip direction of the second ring block inner sealing ring A26 and the second ring block inner sealing ring B28 is toward the valve cover 8 to prevent gas leakage in the suction chamber. The lip direction of the first ring block inner sealing ring A21 is toward the drive structure 19 to prevent the hydraulic oil from continuing to flow to the air guide ring 12. The lip direction of the first ring block inner sealing ring B22 is toward the air guide ring 12 to prevent the gas from continuing to flow to the sleeve part. Through the above-mentioned lip orientation design, the air leakage joint 11 and the oil leakage joint 15 can collect the leaked gas and hydraulic oil respectively. In addition, by distributing multiple sealing rings in series along the axial direction of the push rod 20, the sealing effect can be improved. The grooves in which each sealing ring is embedded are preferably open grooves to facilitate installation and disassembly.

[0082] In order to make the hydraulic oil flow more smoothly to the oil leakage joint 15, as a possible example, in this embodiment, the second oil hole is arranged obliquely relative to the sleeve portion. The second oil hole is located at one end of the inner side surface of the sleeve portion, which is closer to the driving structure 19 than the second oil hole is located at one end of the outer side surface of the sleeve portion.

[0083] When in use, by locating the driving structure 19 above the push rod 20 , the hydraulic oil can flow downwards under the action of gravity and flow outwards along the second oil hole arranged obliquely, so as to facilitate the collection of the hydraulic oil by the oil leakage joint 15 .

[0084] For example, the structure of the unloader can refer to the description of the patent document with publication number CN110206712A, which clamps the end of the push rod 20 away from the driving structure 19 from both sides through the top plate 6 and the pressure cover 29. The top plate 6 and the pressure rod are fixedly connected to the outer shell 5, and the outer shell 5 is fixedly connected to the pressure fork 3, so that the pressure fork 3 and the push rod 20 move synchronously.

[0085] During the ejection stroke of the ejector 20, the ejection state driving force F (hydraulic force or electromagnetic force) provided by the driving structure 19 pushes the ejector 20 to move, and the ejector 20 overcomes the friction force to move, and the ejector plate 6 overcomes the thrust of the return spring 30 to move. When the fork foot of the pressure fork 3 contacts the valve plate 1, the pressure fork 3 overcomes the thrust of the suction valve spring and the gas pressure difference on both sides of the valve plate 1 to move, and then the valve plate 1 opens, and the gas in the compressor flows into the suction chamber. When the outer shell 5 contacts the noise reduction gasket 33 on the valve seat 2, it no longer moves, and the stroke of the pressure fork 3 is L. When the amount of gas refluxed from the compressor to the suction chamber meets the process regulation requirements, the withdrawal stroke of the ejector 20 is opened.

[0086] During the withdrawal stroke of the push rod 20, the pressure fork 3 moves under the help of the pressure difference on both sides and the suction valve spring, the top plate 6 moves under the help of the reset spring 30, and the push rod 20 moves by overcoming the friction force and the withdrawal state driving force F' provided by the driving structure 19. When the pressure fork 3 is separated from the valve plate 1, the valve plate 1 is reset under the action of the suction valve spring and the gas force, the suction chamber is closed, and the compressor begins normal compression, exhaust, expansion and other working processes. The top plate 6 moves under the help of the reset spring 30, and the push rod 20 moves by overcoming the friction force and the driving force provided by the driving structure 19.

[0087] It should be noted that, in order to reduce the impact force during the withdrawal of the push rod 20, the driving force of the driving structure 19 on the push rod 20 cannot be zero during the withdrawal stroke, and the greater the pressure difference on both sides of the valve plate 1, the greater the driving force of the driving structure 19 on the push rod 20. In this embodiment, the driving force in the withdrawal state is 200N to 800N.

[0088] As a possible example, in this embodiment, a calculation process related to selection is also provided to facilitate component selection.

[0089] The calculation process is described in detail below, including the calculation of the driving force F in the ejection state, the driving force F′ in the retraction state, the stiffness k of the return spring 30 and the diameter d of the ejector pin 20 .

[0090] 1) Design parameters

[0091] A={p cy ,p0,p s ,β,A sv ,A l ,f,g,L,α,m,x1,F g2}

[0092] in,

[0093] p cy : During the compressor reflux process, due to gas resistance and other reasons, the surface pressures on both sides of the valve plate 1 are different. Through computer simulation, a gas pressure of about 0.001MPa acts on the valve plate 1;

[0094] p0: standard atmospheric pressure;

[0095] p s : The air pressure in the suction chamber of the compressor;

[0096] β: pressure difference coefficient on both sides of valve plate 1 of the unloader;

[0097] A sv : The area of ​​valve plate 1 (the areas on both sides are the same);

[0098] A l : The cross-sectional area of ​​the top rod 20, d1 is the diameter of the section of the push rod 20 close to the driving structure 19, and the diameter of the section of the push rod 20 away from the driving structure 19 is d2=1.5d1;

[0099] f: friction force on the ejector rod 20;

[0100] g: acceleration due to gravity;

[0101] L: stroke of unloader;

[0102] α: The installation angle of the unloader, which refers to the angle between the center line of the unloader and the vertical line of the ground;

[0103] m: the sum of the masses of the ejector rod 20, the outer shell 5 of the unloader, the top plate 6 of the unloader, the pressure fork 3 of the unloader, and the pressure cover 29 of the unloader;

[0104] x1: pre-compression amount of the return spring 30;

[0105] F g2 : Gas force on valve plate 1, F g2 =β(p cy -p s )A sv ;

[0106] 2) Withdrawal state driving force F′

[0107] In order to reduce the impact force of the actuator during the withdrawal process, the withdrawal state driving force F′ cannot be zero, and the higher the suction pressure, the larger the withdrawal state driving force F′ needs to be to reduce the impact force of the withdrawal process. The withdrawal state driving force F′ is 200N~800N.

[0108] 3) Stiffness k of the return spring 30

[0109] The differential equation of motion for the withdrawal process is as follows:

[0110]

[0111] in,

[0112] Ejection acceleration of the unloader;

[0113] F′: driving force of the unloader withdrawal process (hydraulic force or electromagnetic force provided by the driving structure 19);

[0114] F g1 :Air chamber pressure force, F g1 =(p s -p0)A l ;

[0115] k: stiffness of the return spring 30 of the unloader;

[0116] x: compression amount of the return spring 30 of the unloader;

[0117] The initial conditions of formula 1) are as follows:

[0118]

[0119] in,

[0120] Unloader ejection speed;

[0121] x(0): initial displacement of the unloader during ejection;

[0122] From formula 1) and 2), we can get the displacement equation of the withdrawal process:

[0123]

[0124] in:

[0125] t: represents the movement time of the unloader withdrawal process;

[0126] The boundary conditions of formula 3) are as follows:

[0127] When t = t′ max When x=x1 4)

[0128] in:

[0129] t′ max : Considering the regulating effect of the gas volume regulating system, the value should be within the range of 0.008s to 0.02s;

[0130] The spring stiffness can be obtained from formula 3) and formula 4):

[0131]

[0132] in:

[0133] F s1 :i represents 1, 2, where F s1represents the pre-compression force of the unloader return spring 30, F s2 represents the maximum spring force of the return spring 30 when the unloader moves to the bottom dead center;

[0134] Considering that the unloader can be withdrawn to the upper limit during the withdrawal process, the spring stiffness needs to meet the following conditions:

[0135]

[0136] 4) Ejection state driving force F,

[0137] The differential equation of motion of the ejection process is as follows:

[0138]

[0139] in,

[0140] F: driving force of the unloader ejection process (hydraulic pressure or electromagnetic force provided by the driving structure 19);

[0141] The initial conditions of formula 7) are as follows:

[0142]

[0143] From formula 7) and 8), we can get the displacement equation of the ejection process:

[0144]

[0145] The boundary conditions of formula 9) are as follows:

[0146] When t = t max When x=x1+L 10)

[0147] in:

[0148] t max : Considering the regulating effect of the gas volume regulating system, the value should be within the range of 0.008s to 0.02s;

[0149] The driving force of ejection state is obtained by formula 9) and 10):

[0150]

[0151] 5) Diameter of ejector pin 20

[0152] i: Considering that the ejector pin 20 is subjected to high-frequency and high-intensity impact loads, the diameter should not be less than 10 mm;

[0153] ii: In order to increase the strength of the ejector 20, a variable diameter structure design is adopted, and the diameter d1 of the contact area with the sealing component is consistent with the inner diameter of the sealing component. The diameter needs to be selected with reference to the standard specifications of conventional sealing rings; the diameter of the non-sealing component contact area d2 = 1.5d1;

[0154] iii: The diameter d1 of the ejector pin 20 needs to be calculated using an iterative method:

[0155] Initially, substitute d1=10mm into formula (11) to calculate the driving force in the ejection state;

[0156] If F≤800N, then d1=10mm, and the diameter of the ejector pin 20 is determined;

[0157] If F>800N, the diameter of the push rod 20 needs to be increased, and the diameter of the push rod 20 is increased to d1=12mm;

[0158] Substitute d1=12mm into formula (11) and perform iterative calculation to calculate the driving force in the ejection state;

[0159] If 800N≤F≤1600N, then d1=12mm, and the diameter of the ejector pin 20 is determined;

[0160] If F>1600N, the diameter of the push rod 20 needs to be increased, d1=14mm, the strength is sufficient to meet the use, the iterative calculation is completed, and the diameter of the push rod 20 is determined.

[0161] In order to explain the stress situation more clearly, the following Figure 3 and Figure 4 , and analyze the force conditions of the entire movement process.

[0162] Reference Figure 3 , all the moving parts of the actuator are simplified as a mass block (mass is m), and the actuator forces include: gravity mgcosα, the driving force F in the ejection state, the driving force F′ in the withdrawal state, the elastic force kx of the return spring 30, and the force F acting on the valve plate 1 g2 , the gas pressure in the air chamber exerts a force F on the push rod 20 g1 , friction force f.

[0163] There are four working states of the actuator. The first is the initial state of ejection. The actuator is at the upper limit position, and the compression amount of the return spring 30 is x1. The ejection process occurs during the suction process of the reciprocating compressor. Since the suction valve plate 1 is automatically opened during the suction process, the actuator will not be affected by the valve plate 1 during the ejection process. Therefore, the forces include F, mgcosα, kx1, f, and F g1 ;

[0164] The second is the final state of ejection. Under the action of the ejection state driving force, the actuator moves downward to the lower limit. The compression amount of the return spring 30 is x1+L at this time. The actuator will remain stationary under the action of the ejection state driving force. Therefore, the force includes F, mgcosα, k(x1+L), f, and F g1 .

[0165] The third is the initial state of withdrawal. When the amount of refluxed gas meets the process regulation requirements, the driving force is switched to the driving force F' of the withdrawal state. Under the action of the reset spring 30 and the gas force, the moving parts overcome the driving force F' of the withdrawal state, the friction force, etc., and the moving parts move upward along the guide assembly. The compression amount of the reset spring 30 is x1+L at this time. The initial state of withdrawal is in the compression process. The valve plate 1 of the suction valve is automatically closed and contacts the pressure fork 3. The valve plate 1 will exert an upward force on the pressure fork 3. Therefore, the forces include F, mgcosα, kx1, f, and F. g1 、F g2 .

[0166] The fourth is the final state of withdrawal. Under the push of the reset spring 30, the gas force, and the valve plate 1 force, the actuator moves to the upper limit. The reset spring 30 is compressed by x1 at this time, and the pressure fork 3 is separated from the valve plate 1. The actuator is not affected by the valve plate 1. Therefore, the force includes F, mgcosα, kx1, f, and F g1 ; From state 1 to state 2, the time required is t max , from state three to state four, the time required is t′ max .

[0167] Reference Figure 4 In the initial ejection / final withdrawal state, the compression amount of the return spring 30 is x1, and the elastic force of the return spring 30 is F s1 In the final ejection / initial withdrawal state, the compression amount of the return spring 30 is x1+L, and the elastic force of the return spring 30 is F s2 .

[0168] Referring to the above calculation method, the following is an example of the calculation involved in the component selection of this embodiment in combination with the relevant parameters of two specific compressors. In practical application, it is not limited to the compressor example described below. The calculation process mainly includes:

[0169] (1) Clarify the design parameters, as shown in Table 1, which includes the design parameters of two different compressors:

[0170] Table 1 Energy-saving control system dimensions

[0171]

[0172]

[0173] (2) Based on the data in the first step, the driving force, the elastic force of the return spring 30, the diameter of the push rod 20, etc. are obtained by combining the key parameter design calculation method of the actuator;

[0174] 1. Gas force

[0175] Compressor 1:

[0176] Compressor 2:

[0177] 2. The inlet pressure of reciprocating compressor 1 is low, and the driving force in the withdrawn state is 200N. The inlet pressure of reciprocating compressor 2 is high, and the driving force in the withdrawn state is 500N.

[0178] 3. Stiffness of return spring 30

[0179] t′ max and t max The value is 0.008s, then:

[0180] Compressor 1:

[0181] Solving for k = 51874.75 N / m

[0182] Compressor 2:

[0183] Solving for k = 76137.98 N / m

[0184] Considering that the unloader can be withdrawn to the upper limit during the withdrawal process, the spring stiffness needs to meet the following conditions:

[0185] Compressor 1:

[0186] Compressor 2:

[0187] The stiffness of the return spring 30 in working conditions 1 and 2 both meet the requirements.

[0188] 4. Driving force of ejection state

[0189] Compressor 1:

[0190]

[0191] Compressor 2:

[0192]

[0193] Ejection state driving force constraint conditions: During the ejection holding process, since the actuator needs to be kept in the ejection state, the ejection state driving force needs to be greater than the combined force of gas force, gravity, and maximum displacement spring force. The constraint conditions are as follows:

[0194] Compressor 1: F ≥ F g1 -mgcosα+f+k(x1+L)=412.08N

[0195] Compressor 2: F ≥ F g1 -mgcosα+f+k(x1+L)=900.21N

[0196] The ejection driving force of compressors 1 and 2 meets the requirements.

[0197] 5. Diameter of ejector pin 20

[0198] In "4. Ejection state driving force", if the ejection state driving force of compressor 1 is less than 800N, then:

[0199] d1=10mm,d2=1.5d1=15mm

[0200] The ejection state driving force of compressor 2 is greater than 800N. It is necessary to increase the diameter of ejector rod 20. Substitute d1=12mm into the formula for iterative calculation to calculate the ejection state driving force:

[0201]

[0202] 800N≤F≤1600N, then d1=12mm, and the diameter of the push rod 20 in working condition 2 is determined.

[0203] The present invention uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only used to help understand the method and core ideas of the present invention. At the same time, for those skilled in the art, according to the ideas of the present invention, there will be changes in the specific implementation methods and application scope. In summary, the content of this specification should not be understood as limiting the present invention.

Claims

1. A reciprocating compressor stepless gas volume regulation actuator connecting body structure, characterized in that: include: A push rod, wherein a first end of the push rod is used to connect to a top plate of the unloader, and a second end of the push rod is used to connect to a driving end of a driving structure; A housing, wherein the housing is sleeved on the outside of the push rod and a gap is left between the housing and the push rod; the housing is provided with a first oil hole, and the two ends of the first oil hole are respectively located on the inner side and the outer side of the housing; the first end of the housing is used to connect the valve cover of the compressor; A connecting piece, the connecting piece comprises a flange portion and a sleeve portion; the first side of the flange portion is used to connect to the second end of the shell, the second side of the flange portion is used to connect to the shell of the driving structure, and is in sealing contact with the shell; the sleeve portion is connected to the side of the flange portion away from the driving structure, the sleeve portion is located between the push rod and the shell, and a gap is left between the push rod; the sleeve portion is provided with a second oil hole, the two ends of the second oil hole are respectively located on the inner side and the outer side of the sleeve portion; the second oil hole is butted against the first oil hole; A sealing assembly, the sealing assembly comprising a first end face sealing ring, a second end face sealing ring, a first sealing ring and an oil leakage joint; the first end face sealing ring is used to seal the gap between the first side of the flange portion and the shell, and the second end face sealing ring is used to seal the gap between the valve cover and the shell; the first sealing ring is located between the push rod and the shell, and is located on the side of the sleeve portion away from the drive structure, the inner side surface of the first sealing ring is in sealing contact with the push rod, and the outer side surface of the first sealing ring is in sealing contact with the inner side surface of the shell to seal the gap between the push rod and the shell; the oil leakage joint is connected to the first oil hole, and is used to recover hydraulic oil when the drive structure is a hydraulic cylinder.

2. The connecting body structure of the stepless air volume regulation actuator of the reciprocating compressor according to claim 1 is characterized in that: The sealing assembly also includes an air guide ring and an air leakage joint; the air guide ring is located between the push rod and the shell, and is located on the side of the first sealing ring away from the driving structure, the air guide ring is provided with a first air hole, and the two ends of the first air hole are respectively located on the inner side and the outer side of the air guide ring; the shell is provided with a second air hole, and the two ends of the second air hole are respectively located on the inner side and the outer side of the shell, and the second air hole is connected to the first air hole; the air leakage joint is connected to the second air hole for recovering gas leaked from the compressor.

3. The connecting body structure of the stepless air volume regulation actuator of the reciprocating compressor according to claim 2 is characterized in that: The sealing assembly also includes a second sealing ring; the second sealing ring is located between the push rod and the shell, and is located on the side of the air guide ring away from the drive structure, the inner side surface of the second sealing ring is in sealing contact with the push rod, and the outer side surface of the second sealing ring is in sealing contact with the inner side surface of the shell to seal the gap between the push rod and the shell, so as to reduce the amount of gas leaked from the compressor to the air guide ring.

4. The connecting body structure of the stepless air volume regulating actuator of the reciprocating compressor according to claim 3 is characterized in that: The housing is provided with an inner flange, which is located at a side of the second sealing ring away from the driving structure and is used to limit the circumferential position of the second sealing ring; the push rod passes through the inner flange.

5. The connecting body structure of the stepless air volume regulating actuator of the reciprocating compressor according to claim 3, characterized in that: The second sealing ring includes a second ring block, an inner sealing ring of the second ring block and an outer sealing ring of the second ring block; the second ring block is located between the push rod and the shell, the inner sealing ring of the second ring block is embedded in the inner side surface of the second ring block, and is used for sealing contact with the push rod; the outer sealing ring of the second ring block is embedded in the outer side surface of the second ring block, and is used for sealing contact with the inner side surface of the shell.

6. The connecting body structure of the stepless air volume regulating actuator of the reciprocating compressor according to claim 2, characterized in that: An inner ring groove is provided on the inner side surface of the air guide ring, and an outer ring groove is provided on the outer side surface of the air guide ring; one end of the first air hole is connected to the inner ring groove, and the other end of the first air hole is connected to the outer ring groove.

7. The connecting body structure of the stepless air volume regulating actuator of the reciprocating compressor according to claim 1, characterized in that: The first sealing ring includes a first ring block, an inner sealing ring of the first ring block and an outer sealing ring of the first ring block; the first ring block is located between the push rod and the shell, the inner sealing ring of the first ring block is embedded in the inner side surface of the first ring block, and is used for sealing contact with the push rod; the outer sealing ring of the first ring block is embedded in the outer side surface of the first ring block, and is used for sealing contact with the inner side surface of the shell.

8. The connecting body structure of the stepless air volume regulation actuator of the reciprocating compressor according to claim 1, characterized in that: The second oil hole is arranged obliquely relative to the sleeve portion; the second oil hole is located at one end of the inner side surface of the sleeve portion, which is closer to the driving structure than the second oil hole is located at one end of the outer side surface of the sleeve portion.

9. The connecting body structure of the stepless air volume regulating actuator of the reciprocating compressor according to claim 1, characterized in that: When selecting the return spring of the unloader, the following requirements must be met: When selecting the drive structure, the following requirements must be met: in: p cy : The air pressure in the compressor; p0: standard atmospheric pressure; p s : The air pressure in the suction chamber of the compressor; β: pressure difference coefficient on both sides of the valve plate of the unloader; A sv : The area of ​​the valve plate; A l : the cross-sectional area of ​​the ejector pin, d1 is the diameter of the section of the push rod close to the driving structure, and the diameter of the section of the push rod away from the driving structure is d2=1.5d1; f: the friction force on the ejector rod; g: acceleration due to gravity; L: the stroke of the unloader; α: The installation angle of the unloader, which refers to the angle between the center line of the unloader and the vertical line of the ground; m: the sum of the masses of the ejector rod, the outer shell of the unloader, the top plate of the unloader, the pressure fork of the unloader, and the pressure cover of the unloader; x1: pre-compression amount of the return spring; F g2 : The gas force on the valve plate, F g2 =β(p cy -p s )A sv ; k: the stiffness of the return spring; x: compression amount of the return spring; F′: the driving force exerted by the driving structure on the ejector rod during the withdrawal of the ejector rod; F: The driving force of the driving structure on the ejector during the ejection process of the ejector.

10. The reciprocating compressor stepless gas volume regulation actuator connecting body structure according to claim 9, characterized in that: When selecting the ejector rod, the diameter of the ejector rod is determined by the following iterative calculation method: Initially, substitute d1=10mm into the formula Calculate the driving force in the ejection state; If F≤800N, then d1=10mm, and the diameter of the push rod is determined; If F>800N, the diameter of the push rod needs to be increased, and the diameter of the push rod is increased to d1=12mm; Substitute d1=12mm into formula (11) and perform iterative calculation to calculate the driving force F in the ejection state; If 800N≤F≤1600N, then d1=12mm, and the diameter of the ejector pin is determined; If F>1600N, the diameter of the push rod needs to be increased, d1=14mm, the strength is sufficient to meet the use, the iterative calculation is completed, and the diameter of the push rod is determined.

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