CN113982888A - Energy-saving modification method for high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor - Google Patents
Energy-saving modification method for high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor Download PDFInfo
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/122—Cylinder block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
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Abstract
The utility model discloses an energy-saving modification method of a high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor, which comprises the following steps: the inner diameter of the 1-5-level cylinder body is modified, the split type of the 1-5-level piston is changed into the integral type, and the outer diameter of the 1-5-level piston, the weight of the 1-5-level piston, the outer diameter of the 1-5-level air valve, the outer diameter of the 1-5 valve plate and the clearance of the 1-5-level cylinder body air valve air passage are modified. After the improvement, the air pumping amount of each compressor can be increased by not less than 30%, the original design requirements of the compressor are broken through, the operation power of the compressor is kept unchanged, the energy consumption is not increased, the output of a compressor using enterprise is increased, a large amount of energy is saved, and great economic benefits are achieved.
Description
Technical Field
The utility model belongs to the technical field of energy conservation and environmental protection, and particularly relates to an energy-saving modification method for a high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor.
Background
The large-scale compressor is one of the common equipments in chemical enterprises, and is difficult to modify after installation and use, and the modification difficulty and complexity are well known to those skilled in the art. Moreover, for different models of compressors, the modification method cannot be uniform due to different structures or pressures, and the modification method is modified correspondingly according to different models. For example, the 6M50 type raw material gas compressor is a common reciprocating nitrogen-hydrogen gas compressor (see fig. 1), which is one of the key equipments in chemical enterprises in China, and the total number of the equipments in the country is about 100, and it is necessary to ensure that the equipment operates normally 24 hours a day. Generally, a 6M50 type compressor includes a main motor 100, a multi-stage compression cylinder block 101 in which pistons are provided, and a gas valve 102 provided on the cylinder block 101; the piston and gas valve 102 are important components in the performance of the compressor. The Chinese patent numbers are: 201110332306.3, the utility model patent application named "6M 50 type raw gas compressor increases the gas pumping amount, energy conservation and emission reduction' improves the existing 6M50 type compressor, the improvement method includes the following steps: 1) the pistons in the cylinders of each stage of the compressor are changed from split type to integral type; the piston body of the piston is of an integral structure, and an annular cavity is arranged in the piston body; 2) the thickness of the piston of each stage of cylinder is increased by 0.5 to 0.8 percent on the basis of the existing design standard of the thickness of the piston; 3) the air suction valve and the air discharge valve of each stage of cylinder comprise valve seats, valve plates, springs and lift limiters; the valve seat, the valve plate, the spring and the lift limiter are connected and fixed through a bolt and a nut in sequence; one end of the spring is fixed on the lift limiter, and the other end of the spring props against the back surface of the valve plate, so that the front surface of the valve plate is tightly attached to the valve seat to form a sealing surface; increasing the valve plate lift of the suction valve and the exhaust valve on each stage of cylinder by 11.5-13.6% on the basis of the existing valve plate lift design standard; 4) the equivalent flow area of an intake valve and an exhaust valve on each stage of cylinder is increased by 14.7-15.1% on the basis of the existing equivalent flow area design standard. The method solves the problems of serious piston abrasion and frequent replacement, and also solves the phenomenon that the compressor of the model is pulled by a big horse to be a small car. However, field practice shows that the existing 6M50- (66) -511 can only achieve design requirements, but cannot obtain greater energy-saving effect, so that the original design requirements are broken through.
Disclosure of Invention
The utility model aims to solve the technical problem of providing an energy-saving modification method of a high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor; the energy-saving transformation method can increase the gas production amount by more than or equal to 30 percent, breaks through the original design requirement of the compressor, keeps the operation power unchanged, does not increase the energy consumption, increases the yield for the compressor using enterprises, saves a large amount of energy, and has great economic benefit.
The existing high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor with the pressure of 314kg has the following structural parameters:
the running power of the motor is 5000 kw;
the inner diameter of the primary cylinder body is 1340 mm; the inner diameter of the secondary cylinder body is 820 mm;
the inner diameter of the third-stage cylinder body is 530 mm; the inner diameter of the four-stage cylinder body is 360 mm; the inner diameter of the five-stage cylinder body is 230 mm;
the outer diameter of the primary piston is 1330 mm; the outer diameter of the secondary piston is 811 mm;
the outer diameter of the tertiary piston is 523 mm; the outer diameter of the four-stage piston is 354 mm; the outer diameter of the five-stage piston is 225 mm;
primary piston weight 669 kg; the secondary piston weighs 515 kg;
a tertiary piston weight 313 KG; a four stage piston weight of 313 KG; the weight of the five-stage piston is 186 KG;
the outer diameter of the first-level air valve is 345 mm; the outer diameter of the secondary air valve is 320 mm;
the outer diameter of the three-level air valve is 295 mm; the outer diameter of the four-stage air valve is 185 mm; the outer diameter of the five-stage air valve is 230 mm;
the outer diameter of the first-stage valve plate is 315 mm; the outer diameter of the two-stage valve plate is 292 mm;
the outer diameter of the three-stage valve plate is 261 mm; the outer diameter of the four-stage valve plate is 160 mm; the outer diameter of the five-stage valve plate is 200 mm;
the clearance of the air valve air passage of the 1-3 level cylinder body is 25 mm; the clearance of the air passage of the air valve of the 4-5-level cylinder body is 45 mm.
In order to solve the technical problems, the utility model adopts the following technical scheme：
An energy-saving modification method for a high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor comprises the following steps:
s1, changing the inner diameter of the first-stage cylinder body from 1340mm to 1342-; the inner diameter of the five-stage cylinder body is changed from 230mm to 234 mm and 236 mm;
s2, changing the split type of the piston into the integral type;
the outer diameter of the primary piston is changed to be 1332-1334mm, the outer diameter of the secondary piston is changed to be 813-815mm, the outer diameter of the tertiary piston is changed to be 523-533 mm, and the outer diameter of the quaternary piston is changed to be 362-364 mm; the outer diameter of the five-stage piston is changed from 225mm to 230 mm;
the weight of the primary piston 669KG is changed to 614-616KG, the weight of the secondary piston 515KG is changed to 268-270KG, the weight of the tertiary piston 313KG is changed to 104-106KG, the weight of the quaternary piston 313KG is changed to 104-106KG, and the weight of the quinary piston 186KG is changed to 61-63 KG;
s3, changing the outer diameter 345mm of the first-stage air valve into 347-349mm, the outer diameter 320mm of the second-stage air valve into 322-324mm, the outer diameter 295mm of the third-stage air valve into 304-306mm, the outer diameter 185mm of the fourth-stage air valve into 229-231mm, and the outer diameter 230mm of the fifth-stage air valve into 235-237 mm;
s4, changing the outer diameter of the first-stage valve plate 315mm to 319-298 mm, the outer diameter of the second-stage valve plate 292mm to 296-298mm, the outer diameter of the third-stage valve plate 261mm to 269-271mm, the outer diameter of the fourth-stage valve plate 160mm to 200-202mm, and the outer diameter of the fifth-stage valve plate 200mm to 201-202 mm;
s5, changing the clearance of the air passage of the 1-3 level cylinder air valve from 25mm to 10-13 mm; the clearance of the air passage of the air valve of the 4-5-grade cylinder body is changed from 45mm to 34-36 mm.
Preferably, in step S1, the change of the inner diameter of the primary cylinder from 1340mm to 1342-1343mm is realized by concentric modification through traveling finish grinding.
Preferably, in step S1, the change of the inner diameter of the secondary cylinder from 820mm to 822-823mm is realized by concentric transformation through traveling crane finish grinding.
Preferably, in step S1, the change of the inner diameter of the tertiary cylinder from 530mm to 538-540mm is realized by using vertical lathe machining and finish grinding modification.
Preferably, in step S1, the change of the inner diameter of the four-stage cylinder from 360mm to 368-370mm is directly realized by replacing the cylinder liner in the cylinder.
Preferably, in step S1, the change of the inner diameter of the five-stage cylinder from 230mm to 234 mm and 236mm is directly realized by replacing the cylinder liner in the cylinder.
Preferably, in step S2, the change of the primary piston weight 669kg to 614-616kg is achieved by omitting the pressure-bearing body and changing the piston from split type to integral type.
Preferably, in step S2, the change of the secondary piston weight of 515kg to 268-270kg is realized by replacing the existing raw iron castings JT25-47C with the aluminum alloy L108 subjected to the 500-degree hard oxidation treatment, and changing the piston from split type to integral type.
Preferably, in the step S2, the change of the weight of the three-level piston from 313kg to 104-106kg is realized by replacing the existing raw material iron casting HT250 with the 500-degree hard oxidation treated aluminum alloy L108 and changing the piston from split type to integral type.
Preferably, in step S2, the change of the four-stage piston weight 313KG to 104-106KG is realized by replacing the existing raw material 35# steel with aluminum metal subjected to 800-degree hard oxidation treatment, and changing the piston from split type to integral type.
Preferably, in step S2, the change of the weight 186KG of the five-stage piston to 61 KG to 63KG is realized by replacing the existing raw material 35# steel with aluminum metal subjected to 800-degree hard oxidation treatment, and changing the piston from split type to integral type.
Preferably, in step S5, the change of the clearance of the air passage of the 1-3 stage cylinder air valve from 25mm to 10-13mm is realized by modifying a boring machine.
Preferably, in step S5, the change of the 4-5 stage cylinder air valve air passage clearance from 45mm to 34-36mm is realized by cylinder replacement.
Any range recited herein is intended to include the endpoints and any number between the endpoints and any subrange subsumed therein or defined therein.
The starting materials of the present invention are commercially available, unless otherwise specified, and the equipment used in the present invention may be any equipment conventionally used in the art or may be any equipment known in the art.
The utility model has the following beneficial effects：
1) After the 314kg high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor transformed by the transformation method is actually operated, the gas injection amount can be increased by more than 30 percent under the condition of keeping the existing operation power of 5000kw unchanged (without increasing energy consumption), and the original design requirement of the compressor is broken through, so that the yield of a compressor using enterprise is increased by more than 30 percent, a large amount of energy is saved, and the utility model has great economic benefit.
2) Because the integral piston is adopted to reduce the internal temperature of the compressor, and along with the reduction of the weight of the piston, dead gas in the clearance of the air passage of the air valve of the cylinder body has large rebound force and the like, the service life of the piston ring and the support ring is greatly prolonged.
Drawings
The following detailed description of embodiments of the utility model is provided in connection with the accompanying drawings
FIG. 1 is a schematic diagram of the overall structure of a conventional 6M50- (76) -312 model nitrogen-hydrogen compressor;
FIG. 2 is a schematic cross-sectional view of a cylinder;
fig. 3 is an enlarged schematic view of a part a of the cylinder air valve air passage clearance in fig. 2.
Detailed Description
In order to more clearly illustrate the utility model, the utility model is further described below in connection with preferred embodiments. It is to be understood by persons skilled in the art that the following detailed description is illustrative and not restrictive, and is not to be taken as limiting the scope of the utility model.
It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or be indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or be indirectly connected to the other element.
It will be understood that the terms "length," "width," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like, as used herein, refer to an orientation or positional relationship indicated in the drawings that is solely for the purpose of facilitating the description and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and is therefore not to be construed as limiting the utility model.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.
The utility model provides an energy-saving modification method of a high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor on the basis of the prior art, which comprises the following steps:
s1, changing the inner diameter of the first-stage cylinder body from 1340mm to 1342-; the inner diameter of the five-stage cylinder body is changed from 230mm to 234 mm and 236 mm; it can be understood that, from the above data, the data increase of the three-stage cylinder block and the four-stage cylinder block is larger.
S2, the piston is changed from split type to integral type, the step of changing split type to integral type refers to Chinese patent numbers as follows: 201110332306.3, entitled "6M 50 type raw material gas compressor improvement method for increasing gas production amount, saving energy and reducing emission"; because the split type piston is easier to cause the temperature in the cylinder body to rise, the split type piston is transformed into the integral type by the transformation method of the patent, the transformation can not only reduce the internal temperature of the cylinder body, but also prolong the service life of the piston ring and the support ring;
the outer diameter of the primary piston is changed to be 1332-1334mm, the outer diameter of the secondary piston is changed to be 813-815mm, the outer diameter of the tertiary piston is changed to be 523-533 mm, and the outer diameter of the quaternary piston is changed to be 362-364 mm; the outer diameter of the five-stage piston is changed from 225mm to 230 mm; it can be seen from the data that the increase in the outer diameter of the third stage piston and the fourth stage piston is greater, which is matched with the increase in the inner diameter of the third stage cylinder and the fourth stage cylinder;
the weight of the primary piston 669kg is changed into 614-616kg, and it can be understood that the weight can be slightly changed into light by changing the primary piston from split type to integral type and increasing the annular cavity in the integral piston, but the reduction degree of the weight is not enough only by changing the split type into the integral type, and the reduction degree can also be realized by omitting part of parts (such as a pressure-bearing body and the like);
the weight of the secondary piston is changed from 515kg to 268-270kg, and the step of only changing the weight of the secondary piston from split type to integral type is not enough, because the existing piston material used is iron castings JT25-47C, the piston material is replaced by lighter material (such as 500-degree hard oxidation treated aluminum alloy) from the iron castings JT 25-47C;
the weight of the three-level piston is changed to 104-106kg, and it can be understood that the step of only modifying the three-level piston from split type to integral type is not enough, and because the existing piston material used is the iron casting HT250, the piston material needs to be replaced by a lighter material (such as an aluminum alloy subjected to hard oxidation treatment and the like) from the iron casting HT 250;
the weight of the four-stage piston is changed from 313KG to 106 Kg; it can be understood that the step of modifying the four-stage piston from split type to integral type is not enough, and since the piston material used in the prior art is 35# steel, the piston material needs to be replaced by 35# steel and a lighter material (such as aluminum metal subjected to hard oxidation treatment and the like);
s3, changing the outer diameter 345mm of the first-stage air valve into 347-349mm, the outer diameter 320mm of the second-stage air valve into 322-324mm, the outer diameter 295mm of the third-stage air valve into 304-306mm, the outer diameter 185mm of the fourth-stage air valve into 229-231mm, and the outer diameter 230mm of the fifth-stage air valve into 235-237 mm; the improvement of the outer diameter of the air valve is matched with the improvement of the cylinder body;
s4, changing the outer diameter of the first-stage valve plate 315mm to 319-298 mm, the outer diameter of the second-stage valve plate 292mm to 296-298mm, the outer diameter of the third-stage valve plate 261mm to 269-271mm, the outer diameter of the fourth-stage valve plate 160mm to 200-202mm, and the outer diameter of the fifth-stage valve plate 200mm to 201-202 mm; the outer diameter of the valve plate is improved to be matched with the outer diameter of the air valve;
s5, changing the clearance of the air passage of the 1-3 level cylinder air valve from 25mm to 10-13 mm; the clearance of the air passage of the air valve of the 4-5-grade cylinder body is changed from 45mm to 34-36 mm.
In the utility model, the 'clearance of the air passage of the cylinder air valve' means that: the gap 200 is formed between the edge 1011 of the inner diameter of the cylinder body and the bottom 1021 of the air valve, and for convenience of understanding, the gap data is the shortest distance between the edge 1011 of the inner diameter of the cylinder body and the bottom 1021 of the air valve; that is, the clearance of the air passage of the cylinder air valve is 45mm, which means that the shortest distance between the top point of the edge 1011 of the inner diameter of the cylinder and the bottom 1021 of the air valve is 45mm, as shown in fig. 2 and 3.
Generally speaking, as the transformation of the inner diameter of the cylinder body is increased, the piston is correspondingly enlarged, the load of the whole compressor is increased, and the air-pumping quantity is increased along with the increase of the load, so that the economic value is not high. However, the improvement of the cylinder inner diameter is increased, the piston is correspondingly enlarged, and the existing load 5000kw running power can still be maintained by the following reasons: first, the total weight of the 5 grades of pistons in the present invention decreased from 1996kg to about 1156kg, with a portion of the compressor load decreasing with the weight of the pistons; secondly, changing the clearance of the air passage of the air valve of the 1-3-level cylinder body from 25mm to 10-13 mm; the clearance of the air passage of the 4-5-stage cylinder air valve is changed from 45mm to 34-36mm, so that dead air formed by the existence of the clearance of the air passage of the cylinder air valve in the air passage of the cylinder air valve is changed into live air or free air. That is to say, through practical observation, it is found that gas in the clearance of the air passage of the cylinder air valve is difficult to enter the cylinder body and then enter the cylinder body to be compressed to form product gas, the gas in the clearance of the air passage of the cylinder air valve is dead gas, and each cylinder body has 10 air valves, so that the dead gas in the clearance of the air passage of the cylinder air valve is not a small number, and partial dead gas can be changed into live gas through the transformation of the clearance of the air passage of the cylinder air valve, so that the productivity is improved. In conclusion, by the means, the utility model can increase the air-inflating quantity by more than 30% under the condition of keeping the existing operating power of 5000kw unchanged (without increasing energy consumption), and breaks through the original design requirements of the compressor, thereby increasing the yield by more than 30% for the compressor using enterprises, saving a large amount of energy and having great economic benefit.
As an example, in step S1, the change of the inner diameter of the primary cylinder from 1340mm to 1342-1343mm is achieved by concentric modification through the use of a traveling finish.
As an embodiment, in the step S1, the change of the inner diameter of the secondary cylinder body from 820mm to 822-823mm is realized by performing concentric transformation through traveling finish grinding.
As an embodiment, in the step S1, the change of the inner diameter of the tertiary cylinder body from 530mm to 538-540mm is realized by using vertical lathe machining and finish grinding reconstruction.
As an embodiment, in the step S1, the change of the inner diameter of the four-stage cylinder from 360mm to 368-370mm is directly realized by replacing the cylinder sleeve in the cylinder.
As an embodiment, in the step S1, the change of the inner diameter of the five-stage cylinder from 230mm to 234 mm to 236mm is directly realized through the replacement of the cylinder liner in the cylinder body.
As an embodiment, in step S2, the change of the primary piston weight 669kg to 614-616kg is realized by omitting the pressure-bearing body and changing the piston from split type to integral type.
As an example, in step S2, the change of the secondary piston weight of 515kg to 268-270kg is realized by replacing the existing raw iron castings JT25-47C with aluminum alloy L108 treated by 500 degrees hard oxidation and changing the piston from split type to integral type.
As known to those skilled in the art, the "hard oxidation treatment" is an electrochemical treatment method, and forms a hard oxide film with extreme hardness, high temperature resistance, wear resistance, high electrical resistance and corrosion resistance on the surface of pure aluminum or aluminum alloy material. This technology has been widely used in various industrial and military applications, and is part of the prior art.
As an example, in the step S2, the change of the weight of the three-level piston from 313kg to 104 kg and 106kg is realized by replacing the existing raw iron casting HT250 with the 500-degree hard oxidation treated aluminum alloy L108 and changing the piston from split type to integral type.
As an example, in the step S2, the four-stage piston weight 313KG is changed to 104-106KG by replacing the existing raw material 35# steel with aluminum metal subjected to 800-degree hard oxidation treatment, and the piston is changed from split type to integral type.
As an example, in step S2, the change of the weight 186KG of the five-stage piston to 61 KG to 63KG is performed by replacing the existing raw material 35# steel with aluminum metal subjected to 800 degrees hard oxidation treatment, and changing the piston from split type to integral type.
As an embodiment, in the step S5, the change of the clearance of the air passage of the 1-3 grade cylinder air valve from 25mm to 10-13mm is realized by modifying a boring machine.
As an example, in the step S5, the change of the 4-5 stage cylinder air valve air passage clearance from 45mm to 34-36mm is realized through cylinder replacement.
Example 1
A314 kg high-pressure 6M50- (76) -312 type nitrogen-hydrogen gas compressor of a compressor workshop of Shanxi chemical industry Limited company, which is a group manufactured by Shanxi jin energy-control stock equipment, is modified as follows:
s1, changing the inner diameter of the first-stage cylinder from 1340mm to 1342mm, changing the inner diameter of the second-stage cylinder from 820mm to 822mm, changing the inner diameter of the third-stage cylinder from 530mm to 539mm, and changing the inner diameter of the fourth-stage cylinder from 360mm to 369 mm; the inner diameter of the five-stage cylinder body is changed from 230mm to 235 mm;
s2, changing the split type of the piston into the integral type;
the outer diameter of a first-stage piston is changed from 1330mm to 1333mm, the outer diameter of a second-stage piston is changed from 811mm to 814mm, the outer diameter of a third-stage piston is changed from 523mm to 532mm, and the outer diameter of a fourth-stage piston is changed from 354mm to 363 mm; the outer diameter of the five-stage piston is changed from 225mm to 229 mm;
the weight of a first-stage piston is changed into 615KG, the weight of a second-stage piston is changed into 269KG, the weight of a third-stage piston is changed into 105KG, the weight of a fourth-stage piston is changed into 105KG, and the weight of a fifth-stage piston is changed into 62 KG;
s3, changing the outer diameter 345mm of the first-stage air valve into 348mm, the outer diameter 320mm of the second-stage air valve into 323mm, the outer diameter 295mm of the third-stage air valve into 305mm, the outer diameter 185mm of the fourth-stage air valve into 230mm, and the outer diameter 230mm of the fifth-stage air valve into 236 mm;
s4, changing 315mm of the outer diameter of the first-stage valve plate into 320mm, 292mm of the outer diameter of the second-stage valve plate into 297mm, 261mm of the outer diameter of the third-stage valve plate into 270mm, 160mm of the outer diameter of the fourth-stage valve plate into 201mm, and 200mm of the outer diameter of the fifth-stage valve plate into 201 mm;
s5, changing the clearance of the air passage of the 1-3-level cylinder air valve from 25mm to 12 mm; the clearance of the air passage of the air valve of the 4-5-level cylinder body is changed from 45mm to 35 mm.
In step S1, the change of the inner diameter of the primary cylinder from 1340mm to 1342-mm is realized by performing concentric modification through the traveling finish grinding.
In step S1, the inner diameter of the secondary cylinder body is changed from 820mm to 822mm by concentric transformation through the traveling fine grinding.
In step S1, the change of the inner diameter of the tertiary cylinder from 530mm to 539mm is realized by using vertical lathe machining and line grinding fine modification.
In step S1, the change of the inner diameter of the four-stage cylinder from 360mm to 369mm is directly realized by replacing the cylinder liner in the cylinder.
In step S1, the change of the inner diameter of the five-stage cylinder from 230mm to 235mm is directly realized by replacing the cylinder liner in the cylinder.
In step S2, the change of the primary piston weight 669kg to 615kg is realized by omitting the pressure-bearing body and changing the piston from split type to integral type.
In step S2, the change of the secondary piston weight of 515kg to 269kg is made by replacing the existing raw iron casting JT25-47C with aluminum alloy L108 subjected to hard oxidation treatment at 500 degrees, and changing the piston from split type to integral type.
In step S2, the change of the weight of the three-stage piston from 313kg to 105kg is realized by replacing the existing raw iron casting HT250 with the aluminum alloy L108 subjected to the hard oxidation treatment of 500 degrees, and changing the piston from a split type to an integral type.
In step S2, the change of the four-stage piston weight 313KG to 105KG is realized by replacing the existing raw material 35# steel with aluminum metal subjected to 800-degree hard oxidation treatment, and changing the piston from split type to integral type.
In step S2, the change of the weight 186KG of the five-stage piston to 62KG is achieved by replacing the existing raw material 35# steel with aluminum metal subjected to 800-degree hard oxidation treatment, and changing the piston from split type to integral type.
In step S5, the change of the clearance of the air valve of the 1-3 stage cylinder from 25mm to 12mm is realized by modifying a boring machine.
In step S5, the change of the clearance of the air passage of the 4-5-stage cylinder air valve from 45mm to 35mm is realized by cylinder replacement.
The examination conditions of the 1 improved compressor are as follows:
first, analysis from the viewpoint of energy saving
1) The operating power of the improved compressor is maintained at 5000 kw;
2) the produced product gas (air pumping amount) is increased by 31 percent;
3) the problem of frequent replacement of the piston ring and the support ring is solved;
4) calculating according to the increase of 31% of the air-inflating quantity after modification, namely:
increase the air output per minute by 312m3*0.31＝96.72m3(type 312 means an air-forming quantity of 312 m/min3)
Increase of air pumping quantity per hour by 96.72 x 60 ═ 5803.2m3，
Increasing air pumping quantity 5803.2m every day3*24＝139276.8m3，
The gas production amount is increased to 139276.8m every year3*365＝50836032m3。
Secondly, analyzing from the perspective of saving energy
After the transformation, 64759.62 degrees of electricity per year can be saved under the condition of the same yield,
converted into standard coal saving 64759.62 x 0.36-23313.46 ton/year,
reduce carbon dioxide emissions 23313.46 0.269-6271.32 tons/year,
the emission of sulfur dioxide is reduced by 38183.27 × 0.085 to 1981.64 tons/year.
Those skilled in the art will appreciate that the low pressure 6M50- (66) -511 model Nitrogen Hydrogen gas compressor is approximately nationwide3500Left tableOn the right, therefore, if the machine type is modified in large batch, huge energy materials can be saved, and the discharge of a large amount of harmful gases can be reduced.
It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. Not all embodiments are exhaustive. All obvious changes and modifications which are obvious to the technical scheme of the utility model are covered by the protection scope of the utility model.
Claims (10)
1. The energy-saving transformation method of the high-pressure 6M50- (76) -312 type nitrogen-hydrogen compressor is characterized by comprising the following steps of:
s1, changing the inner diameter of the first-stage cylinder body from 1340mm to 1342-; the inner diameter of the five-stage cylinder body is changed from 230mm to 234 mm and 236 mm;
s2, changing the split type of the piston into the integral type; and is
The outer diameter of the primary piston is changed to be 1332-1334mm, the outer diameter of the secondary piston is changed to be 813-815mm, the outer diameter of the tertiary piston is changed to be 523-533 mm, and the outer diameter of the quaternary piston is changed to be 362-364 mm; the outer diameter of the five-stage piston is changed from 225mm to 230 mm;
the weight of the primary piston 669KG is changed to 614-616KG, the weight of the secondary piston 515KG is changed to 268-270KG, the weight of the tertiary piston 313KG is changed to 104-106KG, the weight of the quaternary piston 313KG is changed to 104-106KG, and the weight of the quinary piston 186KG is changed to 61-63 KG;
s3, changing the outer diameter 345mm of the first-stage air valve into 347-349mm, the outer diameter 320mm of the second-stage air valve into 322-324mm, the outer diameter 295mm of the third-stage air valve into 304-306mm, the outer diameter 185mm of the fourth-stage air valve into 229-231mm, and the outer diameter 230mm of the fifth-stage air valve into 235-237 mm;
s4, changing the outer diameter of the first-stage valve plate 315mm to 319-298 mm, the outer diameter of the second-stage valve plate 292mm to 296-298mm, the outer diameter of the third-stage valve plate 261mm to 269-271mm, the outer diameter of the fourth-stage valve plate 160mm to 200-202mm, and the outer diameter of the fifth-stage valve plate 200mm to 201-202 mm;
s5, changing the clearance of the air passage of the 1-3 level cylinder air valve from 25mm to 10-13 mm; the clearance of the air passage of the air valve of the 4-5-grade cylinder body is changed from 45mm to 34-36 mm.
2. The energy-saving modification method of the nitrogen-hydrogen gas compressor according to claim 1, characterized in that: in step S1, the change of the inner diameter of the primary cylinder from 1340mm to 1342-1343mm is achieved by performing concentric modification through the traveling finish grinding.
3. The energy-saving modification method of the nitrogen-hydrogen gas compressor according to claim 1, characterized in that: in step S1, the internal diameter of the secondary cylinder is changed from 820mm to 822-823mm by concentric transformation through the traveling fine grinding.
4. The energy-saving modification method of the nitrogen-hydrogen gas compressor according to claim 1, characterized in that: in step S1, the change of the inner diameter of the tertiary cylinder from 530mm to 538-540mm is realized by using vertical lathe machining and finish grinding modification.
5. The energy-saving modification method of the nitrogen-hydrogen gas compressor according to claim 1, characterized in that: in step S1, the change of the inner diameter of the four-stage cylinder from 360mm to 368-370mm is directly realized by replacing the cylinder sleeve in the cylinder.
6. The energy-saving modification method of the nitrogen-hydrogen gas compressor according to claim 1, characterized in that: in step S1, the change of the inner diameter of the five-stage cylinder from 230mm to 234 mm and 236mm is directly realized by replacing the cylinder liner in the cylinder.
7. The energy-saving modification method of the nitrogen-hydrogen gas compressor according to claim 1, characterized in that: in step S2, the change of the primary piston weight 669kg to 614-616kg is achieved by omitting the pressure-bearing body and changing the piston from split type to integral type.
8. The energy-saving modification method of the nitrogen-hydrogen gas compressor according to claim 1, characterized in that: in the step S2, the change of the weight of the secondary piston from 515kg to 268-270kg is realized by replacing the existing raw material iron casting JT25-47C with aluminum alloy L108 subjected to 500-degree hard oxidation treatment and changing the piston from split type to integral type;
preferably, in the step S2, the change of the weight of the three-level piston from 313kg to 104-106kg is realized by replacing the existing raw material iron casting HT250 with the 500-degree hard oxidation treated aluminum alloy L108 and changing the piston from split type to integral type.
9. The energy-saving modification method of the nitrogen-hydrogen gas compressor according to claim 1, characterized in that: in step S2, the change of the four-stage piston weight 313KG to 104-106KG is achieved by replacing the existing raw material 35# steel with aluminum metal subjected to 800-degree hard oxidation treatment, and changing the piston from split type to integral type;
preferably, in step S2, the change of the weight 186KG of the five-stage piston to 61 KG to 63KG is realized by replacing the existing raw material 35# steel with aluminum metal subjected to 800-degree hard oxidation treatment, and changing the piston from split type to integral type.
10. The energy-saving modification method of the nitrogen-hydrogen gas compressor according to claim 1, characterized in that: in the step S5, the change of the clearance of the air valve of the 1-3 level cylinder body from 25mm to 10-13mm is realized by modifying a boring machine;
preferably, in step S5, the change of the 4-5 stage cylinder air valve air passage clearance from 45mm to 34-36mm is realized by cylinder replacement.
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