CN107429681B - Liquid-cooled compressor - Google Patents
Liquid-cooled compressor Download PDFInfo
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- CN107429681B CN107429681B CN201680019994.9A CN201680019994A CN107429681B CN 107429681 B CN107429681 B CN 107429681B CN 201680019994 A CN201680019994 A CN 201680019994A CN 107429681 B CN107429681 B CN 107429681B
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- flow path
- oil
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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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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/06—Silencing
Abstract
A liquid-cooled compressor is provided, which reduces vibration of a pipe and noise from a device connected to the pipe with a simple structure. The oil-cooled screw compressor (1) is provided with a compressor main body (11), a liquid supply flow path (14), and a gas buffer unit (20), wherein the compressor main body (11) compresses gas, the liquid supply flow path (14) is communicated with a liquid supply hole (37), the liquid supply hole (37) supplies cooling liquid into a gas compression space (33) formed in the compressor main body, the gas buffer unit (20) is provided with a gas storage unit (28), and the gas storage unit (28) stores gas which receives the pressure of the cooling liquid flowing in the liquid supply flow path.
Description
Technical Field
The present invention relates to a liquid-cooled compressor.
Background
In the liquid-cooled compressor, since the temperature of the fluid rises as the fluid is compressed, the supply of the cooling liquid is performed to cool the compressor main body. For example, in an oil-cooled screw compressor using oil as a coolant, the following cooling is performed.
The oil-cooled screw compressor includes a pair of male and female screw rotors meshing with each other in a rotor casing, and the screw rotors are rotatably supported by bearing portions on the suction side and the discharge side. Oil supply holes are provided in a rotor chamber and a bearing portion, which are gas compression spaces in the screw compressor. The oil supplied to the rotor chamber through the oil supply hole performs a function of cooling the screw rotors and a function of sealing and lubricating the screw rotors with each other and with the inner wall portions of the rotor case.
When the screw rotor rotates, the tooth portion of the screw rotor crosses the oil supply hole provided in the inner wall portion of the rotor case, thereby opening and closing the oil supply hole. The oil supply hole is opened and closed to temporarily shut off the flow of oil, thereby generating pulsation of oil. The pulsation of the oil is transmitted to the piping to which the oil is supplied, and the piping vibrates. Further, due to vibration of the pipe, noise is generated from a device connected to the pipe. As a vibration/seed noise countermeasure technique relating to the conventional art of compressors, for example, patent document 1 is known.
However, in the technique disclosed in patent document 1, a gas pipe is additionally provided, a regulating valve and a stop valve ( り is also used) are provided in each of the gas pipe and the oil injection pipe, and the regulating valve and the stop valve are adjusted so that a certain amount of gas is mixed into the working fluid oil. As described above, the technique disclosed in patent document 1 includes a gas pipe, a regulating valve, and a stop valve, and controls the regulating valve and the stop valve, which is very complicated.
Disclosure of Invention
Accordingly, an object of the present invention is to reduce vibration of a pipe and noise from a device connected to the pipe in a liquid-cooled compressor with a simple configuration.
In order to solve the above-described problems, the present invention provides the following liquid-cooled compressor.
That is, the liquid-cooled compressor of the present invention includes a compressor main body that compresses gas, a liquid supply passage that communicates with a liquid supply hole that supplies coolant to a gas compression space formed in the compressor main body, and a gas buffer unit that includes a gas storage unit that stores gas that receives pressure of the coolant flowing through the liquid supply passage.
According to the above configuration, when the pressure of the coolant flowing through the liquid supply flow path fluctuates and pulsation occurs, the pressure of the pulsation is received by the gas stored in the gas storage portion of the gas buffer portion, and the pulsation can be absorbed and attenuated by the compression action of the gas. As a result, vibration of the pipe and noise from the device connected to the pipe can be reduced by the simple structure.
The present invention can have the following features in addition to the above features.
The gas buffer is provided in at least one of the compressor main body and the liquid supply passage close to the compressor main body. According to this structure, since the gas buffer portion is provided in the vicinity of the source of the pulsation, vibration and noise caused by the pulsation can be suppressed more effectively.
The gas buffer unit is a tubular body branched at a branch portion from the liquid supply passage close to the compressor main body, and a distal end portion of the tubular body is closed. According to this structure, since the conventional piping can be used as the gas buffer portion, the gas buffer portion can be configured simply and at low cost.
The gas buffer portion is branched at a branch portion from the liquid supply passage of the compressor main body, and is a space provided in the compressor main body, and a terminal end portion of the space is closed. According to this structure, the compressor main body can be used as the gas buffer, and the gas buffer can be configured easily and at low cost.
The gas buffer portion is provided to branch from the liquid supply flow path at a branch portion. According to this structure, the liquid supply flow path can be used as the gas buffer, and therefore the gas buffer can be configured easily and at low cost.
The gas storage unit of the gas buffer unit is located above the liquid supply passage where the branch unit is located. According to this structure, the gas contained in the coolant flowing through the liquid supply flow path is retained in the gas storage portion, and therefore the gas buffer portion can operate stably.
The opening of the gas storage section communicating with the gas buffer section is disposed at a position facing the flow direction of the coolant. According to this structure, since the gas contained in the coolant flowing through the liquid supply flow path easily flows into the gas buffer unit, the gas can be easily accumulated in the gas accumulating unit, and the gas buffer unit can be stably operated.
The compressor body has a pair of male and female screw rotors engaged with each other. According to this configuration, a screw compressor is provided that suppresses vibration and noise caused by pulsation at the liquid supply flow path.
According to the present invention, vibration of the pipe and noise from the device connected to the pipe can be reduced with a simple configuration.
Drawings
Fig. 1 is a schematic configuration diagram of a liquid-cooled compressor according to embodiment 1 of the present invention.
Fig. 2 is a schematic configuration diagram of a liquid-cooled compressor according to embodiment 2 of the present invention.
Fig. 3 is a view showing a schematic configuration of a liquid-cooled compressor according to embodiment 3 of the present invention.
Fig. 4 is a view showing a schematic configuration of a liquid-cooled compressor according to embodiment 4 of the present invention.
Fig. 5 is a view showing a schematic configuration of a liquid-cooled compressor according to embodiment 5 of the present invention.
Fig. 6 is a view showing a schematic configuration of a liquid-cooled compressor according to embodiment 6 of the present invention.
Fig. 7 is a view showing a 1 st example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 8 is a schematic perspective view showing a main portion of fig. 7.
Fig. 9 is a view showing a 2 nd example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 10 is a schematic perspective view showing a main portion shown in fig. 9.
Fig. 11 is a view showing a 3 rd example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 12 is a view showing a 4 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 13 is a view showing a 5 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 14 is a view showing a 6 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 15 is a view showing a 7 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 16 is a view showing an 8 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 17 is a view showing a 9 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 18 is a view showing a 10 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 19 is a view showing an 11 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 20 is a view showing a 12 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 21 is a view showing a 13 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 22 is a view showing a 14 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 23 is a schematic view showing a 15 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 24 is a schematic view showing a 16 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 25 is a schematic view showing a 17 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 26 is a schematic view showing an 18 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 27 is a schematic view showing a 19 th example of a main part of a liquid-cooled compressor according to the present invention.
Fig. 28 is a schematic view showing a 20 th example of a main part of a liquid-cooled compressor according to the present invention.
Detailed Description
The liquid-cooled compressor 1 according to the present invention will be described below by using an oil-cooled screw compressor as the liquid-cooled compressor 1.
(embodiment 1)
Referring to fig. 1, a liquid-cooled compressor 1 according to embodiment 1 of the present invention will be described. Fig. 1 shows a schematic configuration of a liquid-cooled compressor 1.
As shown in fig. 1, the liquid-cooled compressor 1 includes, for example, a compressor body 11, an oil separation/recovery unit 13, an oil filter 17, an oil cooler 15, and a temperature adjustment valve 19.
As shown in fig. 23 and the like, for example, the liquid-cooled compressor 1 is an oil-cooled screw compressor that uses oil as a cooling liquid and compresses a gas (for example, air) to be compressed by a pair of male and female screw rotors 34 that mesh with each other. A pair of male and female screw rotors 34 meshing with each other in the oil-cooled screw compressor 1 are accommodated in a rotor chamber (gas compression space) 33 formed in a rotor casing 32 of the compressor main body 11.
As shown in fig. 1, an oil separation/recovery unit 13 is provided in a discharge flow path 12 extending from a compressor body 11. In the case of the oil-cooled screw compressor 1, compressed gas is discharged from the compressor body 11 together with oil, and is separated into compressed gas and oil by the oil separation/recovery unit 13. The compressed gas flows from the portion connected to the discharge flow path 12 in the upper portion of the oil separation/recovery unit 13 to the required equipment. The oil separated in the oil separation/recovery unit 13 is temporarily stored in an oil reservoir formed in the lower portion of the oil separation/recovery unit 13.
In the liquid-cooled compressor 1, a main oil supply passage (liquid supply passage) 14 is formed, and in the main oil supply passage (liquid supply passage) 14, the oil separated by the oil separation/recovery unit 13 flows from the oil separation/recovery unit 13 to the gas compression space of the compressor main body 11. An oil filter 17 and a thermostat valve 19 are provided in this order downstream of the oil separation/recovery unit 13 in the main oil supply passage 14 (hereinafter, simply referred to as the main passage 14). The main channel 14 is branched into a branch cooling channel 14A and a bypass channel 14B at the thermostatic valve 19, and the branch cooling channel 14A and the bypass channel 14B merge at a cooling merging point 51. An oil cooler 15 is disposed in the cooling branch flow path 14A. The temperature adjustment valve 19 allows the oil to flow through the branched cooling passage 14A when the oil temperature is high, and allows the oil to flow through the bypass passage 14B when the oil temperature is low.
The main flow path 14 is provided with an oil supply branching point 52. At the oil supply branch point 52, the bearing oil supply flow passage 21 that passes through the bearing/seed shaft seal portion in the compressor main body 11 branches from the main flow passage 14. The rotor case 32 of the compressor main body 11 is supplied with oil to the rotor chamber (gas compression space) 33 through a main body oil supply hole 37 communicating from a branch point to the main body oil supply passage (liquid supply passage) 18 serving as the downstream side main passage 14. The bearing oil supply hole 39 passing through the bearing oil supply flow path 21 is supplied to the bearing seed shaft seal portion. The oil from the main body oil supply passage 18 is used for cooling the compressed gas, sealing and lubricating the screw rotors 34. The oil from the bearing oil supply passage 21 is used for lubrication of bearings and bearing seals.
Fig. 7 and 8 show a 1 st example of the gas buffer 20. The gas buffer 20 is provided in the middle of the main flow path 14. The gas buffer unit 20 includes a vibration damping main body 24, the vibration damping main body 24 is branched from the main flow path (liquid supply flow path) 14 at a T-shaped pipe joint branched into a branch portion 22, and is connected to the branch portion 22, and the vibration damping main body 24 is a tubular body. The distal end of the damping body 24 is closed by a cover 26. The pipe joint as the branching portion 22 has an inlet 23, an outlet 25, and a branching connection port 27. An upstream pipe of the main flow path 14 is connected to the inlet 23, a downstream pipe of the main flow path 14 is connected to the outlet 25, and the damper main body 24 is connected to the branch connection port 27. A gas storage 28 for storing gas is formed in the inner space of the damper main body 24. When the pressure of the oil flowing through the main flow path 14 fluctuates and pulsation occurs, the pulsating pressure is received by the gas stored in the gas storage portion 28 of the gas buffer portion 20, and the pulsation can be absorbed and attenuated by the compression action of the gas.
In the gas buffer portion 20 shown in fig. 7, the oil flows along the main flow path 14 extending from the lower side to the upper side and then to the right side. The gas storage unit 28 of the gas buffer unit 20 is located above the main flow path 14 located at the branching unit 22. The gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, so that the gas buffer portion 20 can operate stably. The opening of the tubular body passing through the gas storage unit 28 connected to the branch connection port 27 is disposed at a position facing the flow direction of the oil. Since the gas contained in the oil flowing through the main flow passage 14 easily flows into the gas storage portion 28 of the damper main body 24, the gas is easily accumulated in the gas storage portion 28, and the gas buffer portion 20 can stably operate. As a result, the gas accumulated in the gas accumulating portion 28 can suppress vibration and noise caused by pulsation.
The inner diameter of the vibration damping body 24 as a tubular body may be the same as or different from the pipe inner diameter of the main flow passage 14. When the pipe diameters are different, the inner diameter of the damper body 24 can be set to a range from, for example, 0.5 times to 2.0 times the pipe inner diameter of the main passage 14, but is not limited to this value. Further, the gas that has stagnated in the gas accumulating portion 28 of the vibration damping body 24 cannot be easily discharged unless the cover 26 is loosened to actively discharge the gas. Therefore, if the gas storage unit 28 is filled with gas before the liquid-cooled compressor 1 is operated, it is not necessary to wait for the gas contained in the oil flowing through the main flow path 14 to be supplied and stored.
Referring back to fig. 1, the arrangement position of the gas buffer 20 in the main flow path 14 of embodiment 1 will be described. The gas buffer 20 is provided in the main flow path 14 close to the compressor main body 11, that is, at a position midway in the main body oil supply flow path 18 between the main body oil supply hole 37 and the oil supply branch point 52. According to this configuration, since the gas damper 20 is provided in the vicinity of the main body oil supply hole 37 of the compressor main body 11, which is a source of the pulsation, vibration and noise caused by the pulsation can be suppressed more effectively.
Actually, a comparative example not having the gas buffer 20 and the oil-cooled screw compressor 1 of the present invention having the gas buffer 20 were prepared, and vibration values of both when the compressor was operated at a rated rotation speed of 20% were actually measured. Vibration of the main flow path 14 (piping) between the cooling junction 51 and the supply branch point 52 was measured by a vibration analyzer (VA-12, manufactured by shin corporation). As a result, in the oil-cooled screw compressor 1 having the gas buffer portion 20 of the present invention, the total value of the vibration was confirmed to be about 85% smaller than that of the comparative example.
(embodiment 2)
Fig. 2 shows a liquid-cooled compressor 1 according to embodiment 2 of the present invention, and the same reference numerals are given to the same portions as those of the liquid-cooled compressor 1 according to embodiment 1 shown in fig. 1, and the description thereof is omitted. Hereinafter, the same applies to embodiments 3 to 6.
In the liquid-cooled compressor 1 according to embodiment 2, the gas buffer unit 20 is provided at the oil supply branch point 52 of the main flow path 14. At the oil supply branching point 52, the main flow path 14 branches into the main body oil supply flow path 18 and the bearing oil supply flow path 21. By providing the gas buffer unit 20 at the oil supply branch point 52, the change in the conventional structure (i.e., the change in the length of the piping) can be minimized, and therefore, the cost can be reduced. Therefore, in embodiment 2, in addition to suppressing vibration and noise due to pulsation, cost reduction due to minimal changes in the conventional configuration can be achieved.
(embodiment 3)
In the liquid-cooled compressor 1 according to embodiment 3 shown in fig. 3, the oil filter 17 is provided between the cooling junction 51 and the oil supply branch point 52. When embodiment 2 is compared with embodiment 3, only the arrangement position of the oil filter 17 is different, and the other configurations are not different. Like the liquid-cooled compressor 1 according to embodiment 2 described above, the liquid-cooled compressor 1 according to embodiment 3 can also suppress vibration and noise caused by pulsation, and can also be configured with minimal changes.
(embodiment 4)
In the liquid-cooled compressor 1 according to embodiment 4 shown in fig. 4, the gas buffer 20 is provided at a cooling junction 51 of the main flow path 14. When the temperature adjustment valve 19 and the bypass flow path 14B are formed of an integrated component that is integrally formed, the gas buffer 20 is provided at the cooling junction 51 that is the downstream end of the integrated component, whereby vibration and noise caused by pulsation can be suppressed, and the configuration can be changed to the minimum.
(embodiment 5)
In the liquid-cooled compressor 1 according to embodiment 5 shown in fig. 5, a plurality of gas buffers 20 are provided in series at intermediate positions of the main oil supply passage 18 of the main passage 14. With this configuration, the effect of suppressing vibration and noise due to pulsation can be increased.
In the liquid-cooled compressor 1 according to embodiments 1 to 5 described above, for example, the gas buffer units 20 according to examples 2 to 14 shown in fig. 9 to 22 can be used. In embodiments 2 and 3, a cross-shaped pipe joint can be used as the branch portion 22 instead of the T-shaped pipe joint.
First, the gas buffer 20 of example 2 will be described with reference to fig. 9 and 10. The gas buffer unit 20 of example 2 branches from the main flow path (liquid supply flow path) 14 at a T-shaped pipe joint serving as a branch unit 22. The inlet 23 and the outlet 25 of the branch portion 22 are connected to the middle of the main channel 14. The elbow pipe joint 45 passing through the tubular body of the gas storage portion 28 is connected to the branch connection port 27 of the branch portion 22. The damper body 24 is connected to a connection port 47 of the elbow pipe joint 45. That is, the damping body 24 is connected to the branch portion 22 via the elbow pipe joint 45. The gas storage portion 28 of the gas buffer portion 20 is located above the main flow path 14 where the branch portion 22 is located.
In fig. 9, the oil flows along a main flow path 14 extending from the left to the right and then extending in the orthogonal outward direction on the paper. The opening of the tubular body (elbow pipe joint 45) of the gas storage unit 28 that passes through the branch connection port 27 connected to the branch portion 22 is disposed at a position facing the flow direction of the oil. Since the gas contained in the oil flowing through the main flow passage 14 easily flows into the gas storage portion 28 of the damper main body 24, the gas is easily accumulated in the gas storage portion 28, and the gas buffer portion 20 can stably operate. As a result, the gas accumulated in the gas accumulating portion 28 can suppress vibration and noise caused by pulsation.
The gas buffer unit 20 of example 3 shown in fig. 11 branches from the main flow path (liquid supply flow path) 14 at a T-shaped pipe joint serving as a branching unit 22. The vibration damping body 24 is connected to a branch connection port 27 located above the T-shaped branch portion 22. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along a main flow path 14 extending from the left to the right. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
In the gas buffer unit 20 of example 4 shown in fig. 12, a branching unit 22 is used which branches along 3 orthogonal axes of the X, Y, and Z axes. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along a main flow path 14 extending from the left to the right and then extending outward at right angles to the paper. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
The gas buffer unit 20 of example 5 shown in fig. 13 branches from the main flow path (liquid supply flow path) 14 at a Y-shaped pipe joint serving as a branching unit 22. The vibration damping body 24 is connected to a branch connection port 27 located diagonally above and to the right of the Y-shaped branch portion 22. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along a main flow path 14 extending from the lower side to the upper left. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
The gas buffer unit 20 of example 6 shown in fig. 14 branches from the main flow path (liquid supply flow path) 14 at a Y-shaped pipe joint serving as a branching unit 22. The vibration damping body 24 is connected to a branch connection port 27 located diagonally above and to the right of the Y-shaped branch portion 22. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along the main flow path 14 extending from the upper left to the lower side. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
The gas buffer unit 20 of example 7 shown in fig. 15 branches from the main flow path (liquid supply flow path) 14 at a T-shaped pipe joint having a branch connection portion 29 extending obliquely downward to the right as a branch portion 22. The threaded pipe joint 40 is connected obliquely downward to the branch connection port 27 of the branch connection portion 29. The elbow pipe joint 45 is connected to a connection port 46 of the threaded pipe joint 40, and the damper body 24 is connected to a connection port 47 of the elbow pipe joint 45. The inclination angles of the branch connection portion 29 and the nipple 40 are configured such that gas contained in the oil flowing through the main flow passage 14 can be introduced into the gas storage portion 28 of the damper main body 24. The angle of inclination depends on the flow rate of the oil flowing in the main flow path 14, but is, for example, an angle of less than 20 degrees with respect to the main flow path 14 extending in a substantially horizontal transverse direction. The gas reservoir 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along a main flow path 14 extending from the left to the right. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
In the gas buffer portion 20 of example 8 shown in fig. 16, the same members as the branch portions 22 shown in fig. 15 are used, but the pipe length of the threaded pipe joint 40 is short. The shorter the pipe length of the threaded pipe joint 40, the more easily the gas contained in the oil flowing through the main flow passage 14 is introduced into the gas reservoir 28 of the damper main body 24. Since the gas contained in the oil flowing through the main flow path 14 is likely to accumulate in the gas accumulating portion 28, the gas buffer portion 20 can operate stably, and vibration and noise due to pulsation can be suppressed by the gas accumulated in the gas accumulating portion 28.
The gas buffer unit 20 of example 9 shown in fig. 17 branches from the main flow path (liquid supply flow path) 14 at a Y-shaped pipe joint having a branch connection portion 29A extending diagonally upward and rightward as a branch portion 22. The damper main body 24 is connected to the branch connection port 27 of the branch connection portion 29A obliquely upward and rightward. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along the main flow path 14 extending from the upper side to the lower side. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
In the gas buffer portion 20 of the 10 th example shown in fig. 18, the same configuration as the branched portion 22 shown in fig. 17 is used, but the oil flows in the opposite direction to that shown in fig. 17, and the oil flows along the main flow path 14 extending upward from below. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
The gas buffer unit 20 of example 11 shown in fig. 19 branches from the main flow path (liquid supply flow path) 14 at a T-shaped pipe joint serving as a branching unit 22. The vibration damping body 24 is connected to the branch connection port 27 located above the pipe joint via the threaded pipe joint 40 and the elbow pipe joint 45. That is, the elbow pipe joint 45 bent at a right angle is connected to the connection port 46 of the threaded pipe joint 40, and the damper body 24 is connected to the connection port 47 of the elbow pipe joint 45. The vibration damping body 24 is located above the branch portion 22 and extends in a substantially horizontal lateral direction. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along a main flow path 14 extending from the left to the right. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
The gas buffer section 20 of example 12 shown in fig. 20 is similar to the structure shown in fig. 19, but differs in that an elbow pipe joint 45 having a different bending angle is used. In the elbow pipe joint 45 shown in fig. 20, the bending angle is about 45 degrees, but the bending angle may be any angle from 0 to 90 degrees. The damper main body 24 is located above the branching portion 22 and extends obliquely upward. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along a main flow path 14 extending from the left to the right. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
The gas buffer unit 20 of example 13 shown in fig. 21 branches from the main flow path (liquid supply flow path) 14 at a Y-shaped pipe joint having a branch connection portion 29A extending diagonally upward and rightward as a branch portion 22. The damper main body 24 is connected diagonally upward and rightward to the branch connection port 27 of the branch connection portion 29A. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along a main flow path 14 extending from the left to the right. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
The gas buffer unit 20 of example 14 shown in fig. 22 branches from the main flow path (liquid supply flow path) 14 at a Y-shaped pipe joint having a branch connection portion 29A extending obliquely upward and leftward as a branch portion 22. The damper main body 24 is connected diagonally upward and rightward to the branch connection port 27 of the branch connection portion 29A. In the gas buffer portion 20, the gas reservoir portion 28 of the damper main body 24 is located above the main flow path 14 where the branch portion 22 is located. The oil flows along a main flow path 14 extending from the left to the right. Since the gas contained in the oil flowing through the main flow path 14 is retained in the gas storage portion 28, the gas buffer portion 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the gas storage portion 28.
Next, the liquid-cooled compressor 1 according to embodiment 6 will be described with reference to fig. 6 and 23.
(embodiment 6)
In the liquid-cooled compressor 1 according to embodiment 6 shown in fig. 6, the gas buffer 20 is provided inside the rotor casing 32 of the compressor main body 11. An internal oil supply passage 35 is formed as the main passage (liquid supply passage) 14 in the rotor case 32. The internal fuel supply passage 35 is a passage that connects the fuel supply connection hole 36 connected to the main body fuel supply passage 18 and the main body fuel supply hole 37. As shown in fig. 23, in the present embodiment, the internal oil supply flow path 35 is formed so that two main body oil supply holes 37 communicate with one oil supply connection hole 36 provided on the lower side of the rotor case 32. At the rotor case 32, the main body oil supply flow path 18 is connected to the internal oil supply flow path 35 via an oil supply connection hole 36, and oil is supplied to the rotor chamber (gas compression space) 33 through a main body oil supply hole 37.
A vibration damping space 41 is formed inside the rotor case 32 so as to branch from an internal branch point (branch portion) 38 provided in the middle of the internal oil supply passage 35. The damper space 41 according to embodiment 6 is a hollow space formed inside the rotor case 32, and functions as a gas storage portion of the gas damper unit 20. The vibration damping space 41 of example 15 shown in fig. 23 has a curved portion 42 and a longitudinal straight portion 43, and has a lower end side opened at the inner branch point 38 and an upper end side closed. The curved portion 42 extends upward while curving from the inner branch point 38 and communicates with the vertical linear portion 43. The vertical straight portion 43 of the damper space 41, which is a gas reservoir, is located above the internal oil supply passage 35 where the internal branch point 38 is located. Since the bent portion 42 is rounded, the gas contained in the oil flowing through the internal oil supply passage 35 is easily guided to the vibration damping space 41 and accumulated in the vibration damping space 41, and thus the gas buffer portion 20 can stably operate. Further, the gas accumulated in the vibration damping space 41 can suppress vibration and noise caused by pulsation.
In the liquid-cooled compressor 1 according to embodiment 6 described above, the gas buffer unit 20 according to examples 16 to 20 illustrated in fig. 24 to 28 can be used.
In the gas buffer portion 20 of the 16 th example shown in fig. 24, a plurality of vibration damping spaces 41 having a lateral straight portion 48 and a longitudinal straight portion 43 are used. The left and right lateral linear portions 48 extend laterally from the left and right inner branch points 38 and communicate with the left and right longitudinal linear portions 43, respectively. The upper end sides of the left and right longitudinal linear portions 43 are closed, respectively. The vertical straight portion 43 of the damper space 41, which is a gas reservoir, is located above the internal oil supply passage 35 where the internal branch point 38 is located. Since the gas contained in the oil flowing through the internal oil supply passage 35 is retained in the left and right damper spaces 41, the gas buffer unit 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the left and right damper spaces 41.
In the gas buffer unit 20 of the 17 th example shown in fig. 25, a damper space 41 is used which is formed by a curved portion 42 extending upward while being curved from an inner branch point 38. The upper end side of the bent portion 42 shown in fig. 25 is closed. The damper space 41 as a gas storage portion is located above the internal oil supply passage 35 where the internal branch point 38 is located. Since the gas contained in the oil flowing through the internal oil supply passage 35 is retained in the vibration damping space 41, the gas buffer unit 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the vibration damping space 41.
In the gas buffer portion 20 of the 18 th example shown in fig. 26, a vibration damping space 41 having an inclined straight portion 44 and a vertical straight portion 43 is used. The inclined linear portion 44 extends obliquely upward from the inner branch point 38 and communicates with the longitudinal linear portion 43. The upper end side of the longitudinal linear portion 43 is closed. The vertical straight portion 43 of the damper space 41, which is a gas reservoir, is located above the internal oil supply passage 35 where the internal branch point 38 is located. Since the gas contained in the oil flowing through the internal oil supply passage 35 is retained in the vibration damping space 41, the gas buffer unit 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the vibration damping space 41.
In the gas buffer unit 20 of the 19 th example shown in fig. 27, a vibration damping space 41 including an inclined straight portion 44 extending obliquely upward from the inner branch point 38 is used. The upper end side of the inclined straight portion 44 shown in fig. 27 is closed. The inclined straight portion 44 of the damper space 41, which is a gas storage portion, is located above the internal oil supply passage 35 where the internal branch point 38 is located. Since the gas contained in the oil flowing through the internal oil supply passage 35 is retained in the vibration damping space 41, the gas buffer unit 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the vibration damping space 41.
In the gas buffer portion 20 of the 20 th example shown in fig. 28, the damper space 41 is provided to stand up from the internal oil supply passage 35 extending in the lateral direction from the left to the right. The vibration damping space 41 is formed by a vertical linear portion 43 extending upward from the internal branch point 38, and the upper end side of the vertical linear portion 43 is closed. The vertical straight portion 43 of the damper space 41, which is a gas reservoir, is located above the internal oil supply passage 35 where the internal branch point 38 is located. Since the gas contained in the oil flowing through the internal oil supply passage 35 is retained in the vibration damping space 41, the gas buffer unit 20 can operate stably, and vibration and noise caused by pulsation can be suppressed by the gas retained in the vibration damping space 41.
While the present invention has been described with reference to specific configurations and numerals for easy understanding of the present invention, the present invention is not limited to the specific configurations and numerals of the above embodiments, and may include various modifications that can be conceived without departing from the scope of the contents recited in the claims.
In the above-described embodiments 1 to 5, the structure in which the gas is retained in the resonator space 41 formed by the tubular body as the gas buffer portion 20 and the coolant is brought into direct contact with the retained gas will be described. However, as the gas buffer portion 20, a so-called accumulator in which an air bag made of an elastically deformable film such as rubber is filled with gas and the coolant indirectly contacts the gas in the air bag can be used. That is, in the accumulator, the coolant and the gas are separated by the elastic membrane, and the pressure of the coolant is received by the gas through the elastic membrane. This accumulator is used in the oil-cooled screw compressor 1 according to embodiments 1 to 5 described above, and is connected to a pipe constituting the main flow passage 14.
In the above embodiments, the description has been given of the twin-screw compressor incorporating the pair of male and female screw rotors 34 which mesh with each other. The present invention is suitably applied to a compressor having pulsation of oil caused by oil supply interruption due to a tooth portion of the screw rotor 34 crossing the main body oil supply hole (liquid supply hole) 37. Therefore, the present invention can be applied to a single screw compressor in which the gate of the gate rotor is engaged with the spiral groove of the screw rotor, and the oil supply between the wall surface of the spiral groove and the gate is interrupted.
Oil is exemplified as the coolant, but the coolant may be water. Further, air is exemplified as the gas to be compressed, but the gas to be compressed may be nitrogen gas, oxygen gas, natural gas, town gas, hydrocarbon gas, refrigerant gas for refrigerators, or the like.
In embodiments 1 to 5, the gas storage unit 28 of the gas buffer unit 20 is a tubular body connected to a branch pipe branching from the main flow path 14. In embodiment 6, the vibration damping space 41 functioning as the gas storage portion of the gas buffer portion 20 is a hollow formed inside the rotor case 32 of the compressor main body 11. The gas storage portion of the gas buffer portion 20 may include both a tubular body and a cavity.
Description of the reference numerals
1 oil-cooled screw compressor (liquid-cooled compressor)
11 compressor body
12 discharge flow path
13 oil separating and recovering device
14 Main oil supply flow path (liquid supply flow path)
14A cooling branch flow path
14B bypass flow path
15 oil cooler
17 oil filter
18 main body oil supply flow path (liquid supply flow path)
19 temperature regulating valve
20 gas buffer part
21 bearing oil supply flow path
22 branch part
23 inlet
24 vibration damping body (straight pipe)
25 outlet port
26 cover
27 branched connection port
28 gas storage part
29 bifurcated connecting portion
29A bifurcated connecting portion
32 rotor case
33 rotor chamber (gas compression space)
34 screw rotor
35 internal oil supply flow path (liquid supply flow path)
36 oil supply connecting hole
37 main body oil supply hole (liquid supply hole)
38 internal bifurcation point
39 bearing oil supply hole
40 threaded pipe joint
41 vibration damping space
42 bending part
43 longitudinal straight line part
44 inclined straight line part
45 elbow pipe joint
46. 47 connection port
48 transverse straight line part
51 cooling confluence point
Oil is supplied 52 to the bifurcation point.
Claims (8)
1. A liquid-cooled compressor, characterized in that,
comprises a compressor body, a liquid supply passage, and a gas buffer,
the compressor body is provided with a screw rotor for compressing gas,
the liquid supply flow path is communicated with a liquid supply hole formed on the compressor main body and supplies cooling liquid to the gas compression space,
the gas buffer unit is provided in the liquid supply passage, and has a gas storage unit that stores gas that absorbs or attenuates pulsation of the cooling liquid in the liquid supply passage generated when the screw rotor rotates and the flow of the cooling liquid is temporarily interrupted.
2. The liquid-cooled compressor as claimed in claim 1,
the gas buffer is provided in at least one of the compressor main body and the liquid supply passage close to the compressor main body.
3. The liquid cooled compressor as set forth in claim 2,
the gas buffer unit is a tubular body branched from the liquid supply passage close to the compressor main body at a branch portion, and a distal end portion of the tubular body is closed.
4. The liquid cooled compressor as set forth in claim 2,
the gas buffer unit is branched from the liquid supply passage of the compressor main body at a branching portion, and is a space provided in the compressor main body, and a distal end portion of the space is closed.
5. The liquid-cooled compressor as claimed in claim 1,
the gas buffer portion is provided to branch from the liquid supply flow path at a branching portion.
6. Liquid cooled compressor as claimed in any one of claims 3 to 5,
the gas storage unit of the gas buffer unit is located above the liquid supply passage where the branch unit is located.
7. A liquid cooled compressor as claimed in claim 3,
the opening of the gas storage section communicating with the gas buffer section is disposed at a position facing the flow direction of the coolant.
8. The liquid-cooled compressor as claimed in claim 1,
the compressor body has a pair of male and female screw rotors engaged with each other.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015-077257 | 2015-04-03 | ||
| JP2015077257A JP6472700B2 (en) | 2015-04-03 | 2015-04-03 | Liquid-cooled compressor |
| PCT/JP2016/056084 WO2016158152A1 (en) | 2015-04-03 | 2016-02-29 | Liquid-cooled compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107429681A CN107429681A (en) | 2017-12-01 |
| CN107429681B true CN107429681B (en) | 2021-05-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201680019994.9A Active CN107429681B (en) | 2015-04-03 | 2016-02-29 | Liquid-cooled compressor |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6472700B2 (en) |
| CN (1) | CN107429681B (en) |
| WO (1) | WO2016158152A1 (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02153269A (en) * | 1988-12-05 | 1990-06-12 | Electric Power Dev Co Ltd | Pressure pulsation preventing device for piston pump for transporting sand slurry |
| JPH1193875A (en) * | 1997-07-25 | 1999-04-06 | Kobe Steel Ltd | Two-stage oil-cooled screw compressor |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5956312U (en) * | 1982-10-06 | 1984-04-12 | トヨタ自動車株式会社 | side branch type silencer |
| JPH11336683A (en) * | 1998-05-21 | 1999-12-07 | Mayekawa Mfg Co Ltd | Oil-cooled screw compressor |
| JP4062001B2 (en) * | 2001-10-19 | 2008-03-19 | 株式会社デンソー | Gas compression device |
| JP3891844B2 (en) * | 2002-01-10 | 2007-03-14 | 株式会社神戸製鋼所 | Oil-cooled compressor |
| JP4145830B2 (en) * | 2004-04-09 | 2008-09-03 | 株式会社神戸製鋼所 | Oil-cooled compressor |
| CN102016326B (en) * | 2008-03-13 | 2013-09-11 | Aaf-麦克维尔公司 | High capacity chiller compressor |
| JP5650922B2 (en) * | 2010-04-14 | 2015-01-07 | 株式会社神戸製鋼所 | Compressor |
| CN103850941B (en) * | 2012-11-29 | 2017-06-06 | 珠海格力电器股份有限公司 | Compressor fueling injection equipment, compressor, compressor lubrication system and refrigeration system |
-
2015
- 2015-04-03 JP JP2015077257A patent/JP6472700B2/en active Active
-
2016
- 2016-02-29 CN CN201680019994.9A patent/CN107429681B/en active Active
- 2016-02-29 WO PCT/JP2016/056084 patent/WO2016158152A1/en active Application Filing
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02153269A (en) * | 1988-12-05 | 1990-06-12 | Electric Power Dev Co Ltd | Pressure pulsation preventing device for piston pump for transporting sand slurry |
| JPH1193875A (en) * | 1997-07-25 | 1999-04-06 | Kobe Steel Ltd | Two-stage oil-cooled screw compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107429681A (en) | 2017-12-01 |
| JP6472700B2 (en) | 2019-02-20 |
| JP2016196856A (en) | 2016-11-24 |
| WO2016158152A1 (en) | 2016-10-06 |
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Effective date of registration: 20220214 Address after: Tokyo, Japan Patentee after: Shengang Compressor Co.,Ltd. Address before: Kobe City, Hyogo Prefecture, Japan Patentee before: Kobe Steel, Ltd. |