CN111734604A - Liquid piston type gas compressor - Google Patents
Liquid piston type gas compressor Download PDFInfo
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- CN111734604A CN111734604A CN202010723574.7A CN202010723574A CN111734604A CN 111734604 A CN111734604 A CN 111734604A CN 202010723574 A CN202010723574 A CN 202010723574A CN 111734604 A CN111734604 A CN 111734604A
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- cylinder body
- piston
- hydraulic cylinder
- liquid
- gas compressor
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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
- F04B31/00—Free-piston pumps specially adapted for elastic fluids; Systems incorporating such pumps
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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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
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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
- F04B39/0011—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 liquid 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
- F04B39/06—Cooling; Heating; Prevention of freezing
Abstract
The invention relates to a liquid piston type gas compressor, which comprises at least one cylinder body, wherein a hydraulic cylinder body is arranged between the cylinder body and a crankcase, the hydraulic cylinder body is correspondingly communicated with the cylinder body, a piston is arranged in the hydraulic cylinder body, the piston is in sliding fit with the inner wall of the hydraulic cylinder body, the lower end of the piston is connected with a crankshaft through a connecting rod, working liquid is filled above the piston, the working liquid is pushed by the piston to move up and down in the cylinder to form a liquid piston, the liquid piston compresses gas in the cylinder, and a metal heat absorber is arranged in the cylinder body to directly cool the compressed gas. The liquid plunger can play the sealed effect and the transmission power effect of former air compressor machine piston, and the heat absorber is submerged completely to the in-process of liquid plunger up-and-down motion, plays the effect of cooling heat absorber and cylinder wall. The invention improves the cooling capacity of the piston gas compressor as much as possible, leads the compression process of the liquid piston gas compressor to be as close to ideal isothermal compression as possible, and reduces the power consumption of the piston gas compressor.
Description
Technical Field
The invention belongs to the field of gas compressor manufacturing, and particularly relates to a piston type gas compressor.
Background
The existing piston type gas compressor always uses the traditional cylinder and piston structure, and the cooling modes of the existing piston type gas compressor are air cooling and water cooling, both the cooling of the cylinder body and the cooling of the compressed gas are insufficient, the distance between the cylinder body and the ideal isothermal compression is far, and the power consumption is large.
Disclosure of Invention
The invention provides a liquid piston type gas compressor, which at least solves one technical problem in the background technology, and improves the cooling capacity of the piston type gas compressor as much as possible, so that the compression process of the liquid piston type gas compressor is close to ideal isothermal compression as much as possible, and the power consumption of the piston type gas compressor is reduced.
The invention is realized by the following steps: the invention discloses a liquid piston type gas compressor, which comprises at least one cylinder body of the compressor, wherein a hydraulic cylinder body is arranged between each cylinder body and a crankcase, the inner cavity of the hydraulic cylinder body is correspondingly communicated with the inner cavity of the cylinder body, a piston is arranged in the hydraulic cylinder body, the piston is in sliding fit with the inner wall of the hydraulic cylinder body, the lower end of the piston is connected with a crankshaft in the crankcase through a connecting rod, working liquid is filled above the piston, and the working liquid above the piston is pushed by the piston to enter the cylinder body and compress gas in the cylinder body.
The invention discloses a liquid piston type gas compressor, which comprises at least one cylinder body of the compressor, wherein a hydraulic cylinder body is arranged between each cylinder body and a crankcase, the inner cavity of the hydraulic cylinder body is correspondingly communicated with the inner cavity of the cylinder body, a piston is arranged in the hydraulic cylinder body, the piston is in sliding fit with the inner wall of the hydraulic cylinder body, a piston rod is also arranged in the hydraulic cylinder body, the upper end of the piston rod is connected with the piston, the lower end of the piston rod extends into the crankcase from the bottom of the hydraulic cylinder body and is connected with the crankshaft through a connecting rod, working liquid is filled above the piston, and the working liquid above the piston is pushed by the piston to enter the cylinder body and compress gas in the cylinder body.
The invention also discloses a liquid piston type gas compressor, which comprises at least two cylinder bodies of the compressor, wherein each two cylinder bodies form a basic unit, the two cylinder bodies in one basic unit are respectively a cylinder body C and a cylinder body D, a hydraulic cylinder body is arranged between the cylinder body C and a crankcase, the inner cavity of the hydraulic cylinder body is correspondingly communicated with the inner cavity of the cylinder body C, a bidirectional piston is arranged in the hydraulic cylinder body, the piston is in sliding sealing fit with the inner wall of the hydraulic cylinder body, working liquid is filled in the upper space and the lower space of the bidirectional piston in the hydraulic cylinder body, the bottom of the hydraulic cylinder body is sealed, a piston rod outlet is reserved at the bottom of the hydraulic cylinder body, a piston rod is also arranged in the hydraulic cylinder body, the upper end of the piston rod is connected with the bidirectional piston, the lower end of the piston rod extends into the crankcase from the piston rod, the lower part of the hydraulic cylinder body is provided with a liquid passing port, the bottom of the cylinder body D is sealed, the liquid passing port is reserved, and the liquid passing port of the cylinder body D is communicated with the liquid passing port at the lower part of the hydraulic cylinder body through a channel.
And a liquid cooling device is arranged at a channel between the liquid passing port of the cylinder body D and the liquid passing port at the lower part of the hydraulic cylinder body in each basic unit. And metal heat absorbers are respectively arranged in the cylinder body C and the cylinder body D.
On the basis of the three schemes, the following preferred schemes can be provided:
further, a gas cooling device is arranged in the cylinder body; a liquid cooling device is arranged below the gas cooling device; the liquid cooling device is arranged in the cylinder body or the hydraulic cylinder body; when the liquid cooling device is disposed in the cylinder block, the liquid cooling device is located at the bottom of the cylinder block.
Furthermore, the gas cooling device comprises a heat absorber which is coiled by a heat absorbing wire mesh or a heat absorbing sheet into a spiral cylindrical shape, and a gap is reserved between two adjacent side walls in the coiled heat absorbing wire mesh or the coiled heat absorbing sheet to form a channel with a spiral cross section.
Further, the heat absorber which is coiled into a spiral cylindrical shape is filled in the whole cylinder body; the density of the heat absorption wire mesh is more dense the closer the heat absorption wire mesh is to the exhaust port.
Furthermore, the heat absorbing wire mesh is adopted, and the heat absorbing sheet is made of a thin metal sheet.
Furthermore, the inner diameter D of the hydraulic cylinder body is larger than the inner diameter D of the cylinder body, the distance traveled by liquid pressed out by the hydraulic cylinder body in the cylinder body after the liquid correspondingly enters the cylinder body is longer than the distance traveled by the liquid in the hydraulic cylinder body, and the distance traveled by the piston of the hydraulic cylinder body is smaller than the distance traveled by working liquid in the cylinder body.
Further, the working fluid filled in the hydraulic cylinder body is water or other fluid.
Further, liquid cooling device adopts the water chiller, the water chiller includes condenser tube, and condenser tube is located the cylinder body to with the working fluid heat transfer in the cylinder body, the both ends of condenser tube communicate with water inlet, the delivery port that is equipped with on the lateral wall of cylinder body respectively.
Furthermore, the hydraulic cylinder body can be provided with a liquid supplementing port, the liquid supplementing port is communicated with the liquid storage device through a liquid supplementing channel and a liquid supplementing pipeline, and a liquid adding metering pump is arranged on the liquid supplementing pipeline, so that working liquid can be supplemented into the hydraulic cylinder body according to experience or measurement data.
The invention has the following beneficial effects: according to the invention, a hydraulic cylinder body is arranged between the cylinder body and the crankcase, a piston is arranged in the hydraulic cylinder body, the piston is in sliding sealing fit with the inner wall of the hydraulic cylinder body, the lower end of the piston is connected with the crankshaft through a connecting rod, and working liquid is filled above the piston. The invention adopts the piston to push the liquid to move up and down in the cylinder to form the liquid plunger, the original piston is replaced by the liquid plunger, and the liquid plunger can play the roles of sealing and transmitting power of the piston of the original compressor. The improved scheme provided by the invention can greatly reduce the mechanical loss of the original piston by replacing the original piston with the liquid column, and the sealing problem of the piston ring can be thoroughly solved by replacing the original piston with the liquid column liquid piston. In addition, the improved scheme provided by the invention can realize absolute oil-free performance by adopting water as working liquid.
A gas cooling device is arranged in the cylinder body; the gas cooling device comprises a metal heat absorber which is formed by coiling a metal wire mesh or a thin metal sheet into a spiral cylindrical shape, and a gap is reserved between two adjacent side walls of the coiled metal wire mesh or thin metal sheet to form a channel with a spiral cross section. The liquid plunger can axially rise along the spiral cylindrical heat absorber to compress gas in the cylinder body, meanwhile, the heat absorber in the cylinder body directly cools the compressed gas, the actual volume of the heat absorber wire mesh only occupies a small part of the volume of the cylinder and is enough to absorb heat generated by the compressed gas, and the temperature rise of the compressed gas is controlled to be a very low level, so that the compression process is closer to isothermal compression, and the compression power consumption can be effectively reduced. And the invention can cool the spiral cylindrical heat absorber by submerging the spiral cylindrical heat absorber through the ascending liquid.
The improved scheme provided by the invention has the advantages that the cooling mode is continuous, the gas temperature is not too high, the staged compression or the fractional compression is not needed for a high-compression ratio compressor, and a middle cooling device is not needed even for the staged compression.
The invention provides a preferable scheme that the liquid piston type gas compressor comprises basic units consisting of a cylinder body C and a cylinder body D, a hydraulic cylinder body is arranged between the cylinder body C and a crankcase in each basic unit, and a liquid passing port of the cylinder body D in each basic unit is communicated with a liquid passing port at the lower part of the hydraulic cylinder body through a channel. Above-mentioned scheme is all doing work when the bent axle crank throw rotates, the piston upward movement in the hydraulic cylinder body compresses the gas in the cylinder body C promptly, the piston downward movement in the hydraulic cylinder body compresses the gas in the cylinder body D, compare the mode of a general compressor cylinder crank throw, this embodiment bent axle utilization ratio improves, and the bent axle atress has not been increased, each crank throw corresponds two cylinders, can reduce the crank throw quantity, and then reduce complete machine length, weight, the diameter that increases the pneumatic cylinder can play the effect of increasing the cylinder stroke equally.
Drawings
FIG. 1 is a schematic structural diagram of a first embodiment of a liquid piston gas compressor according to the present invention;
fig. 2 is a schematic structural view of a third embodiment of the liquid piston gas compressor of the present invention.
In the drawing, 1 is a cylinder block, 2 is a hydraulic cylinder block, 3 is a heat absorber, 41 is a piston, 42 is a bidirectional piston, 5 is a working fluid, 6 is a piston rod, 7 is a connecting rod, 8 is a crankshaft, 9 is a passage, 10 is an intake valve, 11 is an exhaust valve, and 12 is a water cooler.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention.
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 otherwise specified.
Example one
Referring to fig. 1, the embodiment discloses a liquid piston type gas compressor, which includes at least one cylinder block 1, a hydraulic cylinder block 2 is disposed between each cylinder block 1 and an upper crankcase, the hydraulic cylinder block 2 is correspondingly communicated with the cylinder block 1, a piston 41 is disposed in the hydraulic cylinder block 2, the piston 41 is in sliding fit with an inner wall of the hydraulic cylinder block 2, a piston rod 6 is further disposed in the hydraulic cylinder block 2, an upper end of the piston rod 6 is connected with the piston 41, a lower end of the piston rod 6 extends into the crankcase from the hydraulic cylinder block 2 and is connected with a crankshaft 8 through a connecting rod 7, a certain amount of working liquid 5 is filled above the piston 41, and the piston 41 pushes the working liquid 5 above to make the working liquid 5 enter the cylinder block 1 and compress gas in the cylinder block 1.
Further, a gas cooling device is arranged in the cylinder block 1; a liquid cooling device is arranged below the gas cooling device; the liquid cooling device is provided in the cylinder block 1 or the hydraulic cylinder block 2. The liquid cooling device of the embodiment is arranged at the bottom of the cylinder block 1 and is connected with the hydraulic cylinder block 2.
Furthermore, the gas cooling device comprises a heat absorber which is coiled by a heat absorbing wire mesh or a heat absorbing sheet into a spiral cylindrical shape, and a gap is reserved between two adjacent side walls in the coiled heat absorbing wire mesh or the coiled heat absorbing sheet to form a channel with a spiral cross section.
Furthermore, the heat absorbing wire mesh is adopted, and the heat absorbing sheet is made of a thin metal sheet. The metal heat absorber is coiled into a spiral cylindrical shape by a metal wire mesh or a thin metal sheet. Of course, the material of the heat absorbing wire mesh and the heat absorbing sheet of the invention is not limited to metal, and other heat absorbing materials can be selected according to actual needs.
Further, a metal heat absorber coiled in a spiral cylindrical shape is filled in the entire cylinder block 1; the density of the heat absorption wire mesh is more dense the closer the heat absorption wire mesh is to the exhaust port.
The density of the heat absorber wire mesh and the interlayer gap (a gap is reserved between two adjacent side walls) are determined by the compression ratio. The larger the compression ratio, the higher the wire mesh density and the interlayer gap density are, so as to ensure the heat absorber to have enough heat capacity. The density of the wire mesh is closer to the exhaust port and denser, so that the heat absorber has enough heat capacity in the later compression stage.
Since the specific gravity of the metal is much greater than that of the gas and the specific heat is not much different (in the case of stainless steel, air, the specific gravity is about 6000 times and the specific heat of the gas is only about 2.5 times that of stainless steel), the actual volume of the heat absorber wire mesh occupying only a small portion of the cylinder volume is sufficient to absorb the heat generated by the compressed gas and control the temperature of the compressed gas to a low level. Making the compression process closer to isothermal compression. The density and the interlayer clearance of the heat absorber wire mesh are determined by the compression ratio. The larger the compression ratio, the higher the wire mesh density and the interlayer gap density are, so as to ensure the heat absorber to have enough heat capacity. The closer density of wire mesh is big from the gas vent, and the silk mesh warp interval is unchangeable promptly, and the closer density of weft density is big from the gas vent, improves first half section thermal capacity to guarantee that the heat absorber has sufficient thermal capacity in compression later stage.
The liquid cooling device adopts a water cooler 12, the water cooler 12 comprises a cooling water pipe, the cooling water pipe is positioned in the cylinder body 1 and exchanges heat with the working liquid 5 in the cylinder body 1, and two ends of the cooling water pipe are respectively communicated with a water inlet and a water outlet which are arranged on the side wall of the cylinder body 1.
The piston 41 in the hydraulic cylinder body 2 of the invention pushes the working fluid 5 to move up and down in the cylinder to form a fluid plunger to compress gas in the cylinder, and a metal heat absorber is arranged in the cylinder body 1 to directly cool the compressed gas. The liquid plunger can play the sealing and power transmission roles of the original air compressor piston 41, and the heat absorber is completely submerged by the liquid plunger in the up-and-down movement process, so that the heat absorber and the cylinder wall are cooled.
Further, the inner diameter D of the hydraulic cylinder 2 is larger than the inner diameter D of the cylinder block 1, and the distance traveled by the hydraulic fluid 5 pressed out by the hydraulic cylinder 2 in the cylinder block 1 after entering the cylinder block 1 is longer than the distance traveled by the hydraulic cylinder 2, so that the distance traveled by the piston 41 of the hydraulic cylinder 2 is shorter than the distance traveled by the hydraulic fluid 5 in the cylinder block 1. Of course, the diameter of the hydraulic cylinder can be larger than that of the cylinder, or slightly smaller than or equal to that of the cylinder.
Further, the upper part of the cylinder block 1 is fixedly connected with a cylinder head, and the cylinder head is provided with an intake valve 10 and an exhaust valve 11.
Further, the cylinder body 1, the hydraulic cylinder body 2 and the crankcase are connected into a whole; and the cylinder block 1 is positioned at the upper end of the hydraulic cylinder block 2, and the hydraulic cylinder block 2 is positioned at the upper end of the crankcase. Preferably, the cylinder block 1, the hydraulic cylinder block 2, and the crankcase are cast integrally. A liquid cooling device is provided at a position between the cylinder block 1 and the hydraulic cylinder block 2.
Of course, the following scheme can also be adopted: the hydraulic cylinder body 2 and the upper crankcase are cast into a whole; the hydraulic cylinder body 2 is positioned on the side edge of the cylinder body 1, the bottom of the cylinder body 1 is sealed, and the cylinder body 1 is communicated with the hydraulic cylinder body 2 through a channel 9; a liquid cooling device is arranged at the passage 9 between the cylinder block 1 and the hydraulic cylinder block 2.
Further, the working fluid 5 filled in the hydraulic cylinder 2 may be water or other fluid.
Furthermore, the hydraulic cylinder body 2 can be provided with a liquid supplementing port which is communicated with the liquid storage device through a liquid supplementing channel 9 and a liquid supplementing pipeline, and a liquid adding metering pump is arranged on the liquid supplementing pipeline, so that working liquid 5 can be supplemented into the hydraulic cylinder body 2 according to experience or measurement data.
Other technical features of the liquid piston gas compressor of this embodiment are not improved and may be the same as the existing piston gas compressor.
Example two
The embodiment discloses a liquid piston type gas compressor, which comprises a cylinder body and a crankcase, wherein a hydraulic cylinder body is arranged between the cylinder body and the upper crankcase and correspondingly communicated with the cylinder body, a piston is arranged in the hydraulic cylinder body and is in sliding fit with the inner wall of the hydraulic cylinder body, the lower end of the piston is connected with a crankshaft through a connecting rod, a certain amount of working liquid is filled above the piston, and the working liquid above the piston is pushed by the piston to enter the cylinder body and compress gas in the cylinder body.
Other technical features of the present embodiment are the same as those of the first embodiment.
EXAMPLE III
Referring to fig. 2, the embodiment discloses a liquid piston type gas compressor, which comprises at least one basic unit, each basic unit comprises a cylinder block C and a cylinder block D, a hydraulic cylinder block 2 is arranged between the cylinder block C and a crankcase, the bottom of the hydraulic cylinder block 2 in each basic unit is sealed, a piston rod outlet is reserved for the piston rod 6 to extend out, the piston rod 6 is in movable sealing fit with the piston rod outlet, a bidirectional piston 42 is arranged in the hydraulic cylinder block 2 in each basic unit, the bidirectional piston 42 is in sliding fit with the inner wall of the hydraulic cylinder block 2, the upper space and the lower space of the bidirectional piston 42 in the hydraulic cylinder block 2 in the basic unit are filled with a certain amount of working liquid 5, the piston rod 6 is further arranged in the hydraulic cylinder block 2 in the basic unit, the upper end of the piston rod 6 is connected with the bidirectional piston 42, the lower end of the piston rod 6 extends into the, the connecting rod 7 is connected with a crankshaft 8 through a connecting rod 7, and the connecting rod 7 is used for converting the rotation motion of the crankshaft 8 into the reciprocating linear motion of a piston; the lower part of the hydraulic cylinder body 2 in the basic unit is provided with a liquid passing port, the bottom of the cylinder body D in each basic unit is sealed, the liquid passing port is reserved, and the liquid passing port of the cylinder body D in each basic unit is communicated with the liquid passing port at the lower part of the hydraulic cylinder body 2 through a channel 9. A liquid cooling device is arranged on a channel 9 between the liquid passing port of the cylinder body D and the liquid passing port at the lower part of the hydraulic cylinder body 2 in each basic unit.
Further, gas cooling devices are arranged in the cylinder body C and the cylinder body D; and a liquid cooling device is arranged below the gas cooling device.
The liquid cooling device described in the present embodiment is provided at the bottom of the cylinder block 1.
The structure of the gas cooling device of the present embodiment is the same as that of the gas cooling device of the first embodiment.
The liquid cooling device of the present embodiment has the same structure as the liquid cooling device of the first embodiment.
The mode of hinging the piston rod 6 and the connecting rod 7 can be the same as the mode of hinging the original piston and the connecting rod, and of course, the mode can be adjusted according to actual requirements.
Further, the inner diameter D of the hydraulic cylinder 2 is larger than the inner diameter D of the cylinder block C, and the distance traveled by the working fluid 5 pressed out by the hydraulic cylinder 2 in the cylinder block 1 after entering the cylinder block C is longer than the distance traveled by the working fluid 5 in the hydraulic cylinder 2, so that the distance traveled by the piston of the hydraulic cylinder 2 is shorter than the distance traveled by the working fluid 5 in the cylinder block C.
When the diameter D of the hydraulic cylinder block 2 is larger than the diameter D of the cylinder block C, since the diameter of the hydraulic cylinder block 2 is large and the diameter of the cylinder block C is small, the distance traveled by the hydraulic fluid 5 pressed out by the hydraulic cylinder block 2 in the cylinder block C after entering the cylinder block 1 is longer than the distance traveled in the hydraulic cylinder block 2. The distance traveled by the piston of the hydraulic cylinder 2 is thus less than the distance of the liquid column in the cylinder block C. Of course, the diameter of the hydraulic cylinder may be larger than that of the cylinder block C or slightly smaller than or equal to that of the cylinder block C.
Further, the upper part of the cylinder block 1 is fixedly connected with a cylinder head, and the cylinder head is provided with an intake valve 10 and an exhaust valve 11.
Further, the cylinder block 1, the hydraulic cylinder block 2 and the crankcase are cast into a whole from top to bottom; and the cylinder block 1 is positioned at the upper end of the hydraulic cylinder block 2, and the hydraulic cylinder block 2 is positioned at the upper end of the crankcase. A liquid cooling device is provided at a position between the cylinder block 1 and the hydraulic cylinder block 2.
Of course, the following scheme can also be adopted: the hydraulic cylinder body 2 and the upper crankcase are cast into a whole; the hydraulic cylinder body 2 is positioned on the side edge of the cylinder body 1, the bottom of the cylinder body 1 is sealed, and the cylinder body 1 is communicated with the hydraulic cylinder body 2 through a channel 9; a liquid cooling device is arranged at the passage 9 between the cylinder block 1 and the hydraulic cylinder block 2.
Further, the working fluid 5 filled in the hydraulic cylinder 2 may be water or other fluid.
Further, the hydraulic cylinder body 2 of the present invention may be provided with a fluid infusion port, and the specific technical features thereof are the same as those of the first embodiment.
Other technical features of the liquid piston gas compressor of the present embodiment may be the same as those of the existing piston gas compressor.
When the piston in the hydraulic cylinder block 2 moves upward, the working fluid 5 above the bidirectional piston 42 enters the cylinder block C, and the working fluid 5 in the cylinder block D returns to the lower portion of the bidirectional piston 42 through the passage 9. At this time, the gas in the cylinder block C is compressed, and the cylinder block D is in an intake state. At this time, the pressure of the compressed gas in the cylinder block C increases, and the gas receives an increase in compression temperature. But because of the existence of the heat absorber, the cylinder wall and the liquid piston, the heat capacity of the heat absorber, the cylinder wall and the liquid piston is far larger than the heat generated by gas compression, and the heat generated by the compressed gas can be absorbed sufficiently to control the temperature rise. When the gas pressure reaches the rated pressure, the gas starts to be discharged from the exhaust valve 11, the bidirectional piston 42 in the hydraulic cylinder 2 continues to move upwards, and the cylinder block C is continuously exhausted until the exhaust process of the cylinder block C is finished when the bidirectional piston 42 moves to reach the upper end point. When the bidirectional piston 42 reaches the upper end point, it starts to move down along the hydraulic cylinder 2, and the exhaust valve 11 is automatically closed. When the gas pressure in the cylinder block C is lower than the suction pressure, the intake valve 10 is automatically opened, the low-pressure gas enters the cylinder block C again, and when the bidirectional piston 42 in the hydraulic cylinder block 2 moves down to the lower end point, the cylinder block C is filled with the gas again, and at this time, the suction process is completed and the next compression process is ready to be completed. When the piston in the hydraulic cylinder block 2 moves down, the working fluid 5 below the bidirectional piston 42 is pushed into the cylinder block D through the passage 9, and the gas in the cylinder block D starts to be compressed. At this time, the gas in the cylinder block D is compressed, and the cylinder block C is in an intake state. At this time, the pressure of the compressed gas in the cylinder block D increases, and the gas receives a compression temperature increase. But because of the existence of the heat absorber, the cylinder wall and the liquid piston, the heat capacity of the heat absorber, the cylinder wall and the liquid piston is far larger than the heat generated by gas compression, and the heat generated by the compressed gas can be absorbed sufficiently to control the temperature rise. When the gas pressure reaches the rated pressure, the gas starts to be discharged from the exhaust valve 11, the bidirectional piston 42 in the hydraulic cylinder body 2 continues to move downwards, and the cylinder body D continuously exhausts the gas until the exhaust process of the cylinder body D is finished when the piston moves to reach the lower end point. In the process of continuously ascending the liquid piston to compress the gas, the cylinder wall and the heat absorber are submerged to cool the gas, the cylinder wall is completely discharged out of the cylinder when the gas is completely discharged out of the cylinder, the heat of the heat absorber is completely absorbed by the working liquid 5, and the temperature returns to the initial state.
The whole process is all doing work when the bent axle 8 throw of this embodiment rotates, namely two-way piston 42 when hydraulic cylinder body 2 in moves upwards and compresses the gas in cylinder block C, two-way piston 42 when hydraulic cylinder body 2 in moves downwards and compresses the gas in cylinder block D, compare the mode of general compressor one jar one throw, this embodiment bent axle 8 utilization ratio improves, and do not increase bent axle 8 atress, each throw corresponds two cylinders, can reduce the throw quantity, and then reduce complete machine length, weight, increase the diameter of pneumatic cylinder can play the effect of increasing the cylinder stroke equally.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (10)
1. A liquid piston gas compressor comprising a cylinder block of at least one compressor, characterized in that: be equipped with hydraulic cylinder body between each cylinder body and the crankcase, the inner chamber of hydraulic cylinder body corresponds the intercommunication with the inner chamber of cylinder body, the internal piston that is equipped with of hydraulic cylinder, the inner wall sliding fit of piston and hydraulic cylinder body, the lower extreme of piston is connected with the bent axle in the crankcase through the connecting rod, the top of piston is filled with working liquid, promotes the working liquid of top through the piston, makes working liquid get into the cylinder body and compress the gas in the cylinder body.
2. A liquid piston gas compressor comprising a cylinder block of at least one compressor, characterized in that: be equipped with hydraulic cylinder body between each cylinder body and the crankcase, the inner chamber of hydraulic cylinder body corresponds the intercommunication with the inner chamber of cylinder body, the internal piston that is equipped with of hydraulic cylinder, the inner wall sliding fit of piston and hydraulic cylinder body, still be equipped with the piston rod in the hydraulic cylinder body, the upper end and the piston connection of piston rod, the lower extreme of piston rod stretches into in the crankcase from the piston rod export of hydraulic cylinder body bottom, is connected with the bent axle through the connecting rod, the top of piston is filled with working liquid, promotes the working liquid of top through the piston, makes working liquid get into the cylinder body and compress the gas in the cylinder body.
3. A liquid piston gas compressor comprising a cylinder block of at least two compressors, characterized in that: every two cylinder bodies form a basic unit, the two cylinder bodies in one basic unit are respectively a cylinder body C and a cylinder body D, a hydraulic cylinder body is arranged between the cylinder body C and a crankcase, the inner cavity of the hydraulic cylinder body is correspondingly communicated with the inner cavity of the cylinder body C, a bidirectional piston is arranged in the hydraulic cylinder body and is in sliding fit with the inner wall of the hydraulic cylinder body, working liquid is filled in the upper space and the lower space of the bidirectional piston in the hydraulic cylinder body, the bottom of the hydraulic cylinder body is sealed, a sealed outlet of the piston rod is reserved at the bottom of the hydraulic cylinder body, a piston rod is further arranged in the hydraulic cylinder body, the upper end of the piston rod is connected with the bidirectional piston, the lower end of the piston rod extends into the crankcase from the outlet of the piston rod at the bottom of the hydraulic cylinder body and is connected with a crankshaft through a connecting rod, and a liquid passing port is reserved, and the liquid passing port of the cylinder body D is communicated with the liquid passing port at the lower part of the hydraulic cylinder body through a channel.
4. A liquid piston gas compressor according to claim 1, 2 or 3, characterised in that: a gas cooling device is arranged in the cylinder body; a liquid cooling device is arranged below the gas cooling device; the liquid cooling device is arranged in the cylinder body or the hydraulic cylinder body; when the liquid cooling device is disposed in the cylinder block, the liquid cooling device is located at the bottom of the cylinder block.
5. The liquid piston gas compressor according to claim 4, wherein: the gas cooling device comprises a heat absorber which is coiled by a heat absorbing wire mesh or a heat absorbing sheet into a spiral cylindrical shape, and a gap is reserved between two adjacent side walls in the coiled heat absorbing wire mesh or the coiled heat absorbing sheet to form a channel with a spiral cross section.
6. The liquid piston gas compressor according to claim 5, wherein: the heat absorber which is coiled into a spiral cylindrical shape is filled in the whole cylinder body; the density of the heat absorption wire mesh is more dense the closer the heat absorption wire mesh is to the exhaust port.
7. The liquid piston gas compressor according to claim 5, wherein: the heat absorbing wire mesh is a metal wire mesh; the heat absorbing sheet is made of thin metal sheet.
8. A liquid piston gas compressor according to claim 1, 2 or 3, characterized in that: the inner diameter D of the hydraulic cylinder body is larger than the inner diameter D of the cylinder body, the walking distance of the working liquid pressed out by the hydraulic cylinder body in the cylinder body after entering the cylinder body is longer than the walking distance of the working liquid in the cylinder body, and the walking distance of the piston of the hydraulic cylinder body is smaller than the walking distance of the working liquid in the cylinder body.
9. A liquid piston gas compressor according to claim 1, 2 or 3, characterized in that: the cylinder body, the hydraulic cylinder body and the crankcase are connected into a whole; and the cylinder body is positioned at the upper end of the hydraulic cylinder body, and the hydraulic cylinder body is positioned at the upper end of the crankcase.
10. A liquid piston gas compressor according to claim 1, 2 or 3, characterized in that: the working fluid filled in the hydraulic cylinder body adopts water or other liquid.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010723574.7A CN111734604A (en) | 2020-07-24 | 2020-07-24 | Liquid piston type gas compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010723574.7A CN111734604A (en) | 2020-07-24 | 2020-07-24 | Liquid piston type gas compressor |
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| Publication Number | Publication Date |
|---|---|
| CN111734604A true CN111734604A (en) | 2020-10-02 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010723574.7A Withdrawn CN111734604A (en) | 2020-07-24 | 2020-07-24 | Liquid piston type gas compressor |
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| Country | Link |
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| CN (1) | CN111734604A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114576140A (en) * | 2022-03-02 | 2022-06-03 | 重庆气体压缩机厂有限责任公司 | Circulating fluid infusion type compression system |
-
2020
- 2020-07-24 CN CN202010723574.7A patent/CN111734604A/en not_active Withdrawn
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114576140A (en) * | 2022-03-02 | 2022-06-03 | 重庆气体压缩机厂有限责任公司 | Circulating fluid infusion type compression system |
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Application publication date: 20201002 |