CN112648168A - Reciprocating compression expander - Google Patents
Reciprocating compression expander Download PDFInfo
- Publication number
- CN112648168A CN112648168A CN202011555685.8A CN202011555685A CN112648168A CN 112648168 A CN112648168 A CN 112648168A CN 202011555685 A CN202011555685 A CN 202011555685A CN 112648168 A CN112648168 A CN 112648168A
- Authority
- CN
- China
- Prior art keywords
- valve
- pressure
- fluid
- piston
- cylinder
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
- F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
- F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
- F04B37/12—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
- F01B1/01—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with one single cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B25/00—Regulating, controlling, or safety means
- F01B25/02—Regulating or controlling by varying working-fluid admission or exhaust, e.g. by varying pressure or quantity
- F01B25/08—Final actuators
- F01B25/10—Arrangements or adaptations of working-fluid admission or discharge valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B29/00—Machines or engines with pertinent characteristics other than those provided for in preceding main groups
- F01B29/08—Reciprocating-piston machines or engines not otherwise provided for
- F01B29/10—Engines
-
- 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
- F04B39/10—Adaptations or arrangements of distribution members
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Fluid-Driven Valves (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
The invention can eliminate the large-scale device, resist the strong elasticity for closing the valve, and according to the load of the reciprocating compression-expansion machine, the valve can be easily opened with a simple mechanism and a low driving force. The reciprocating compressor-expander of the present invention comprises: a 1 st valve and a 2 nd valve (8), wherein the 1 st valve sucks the low-pressure compressible fluid into the main cylinder from the low pressure path after opening, compresses the compressible fluid sucked from the 1 st valve by the action of the main piston to make the fluid become high pressure, the 2 nd valve (8) discharges the compressible fluid to the high pressure path (9) after opening, or the 2 nd valve (8) flows the high-pressure compressible fluid into the main cylinder from the high pressure path after opening, expands the compressible fluid flowing from the 2 nd valve to become low pressure by the action of the main piston, and the 1 st valve discharges the compressible fluid to the low pressure path after opening; a 1 st valve driving mechanism driven by oil pressure or electricity to drive the 1 st valve and the 2 nd valve; and a 2 nd valve drive mechanism (17, 18, 27) for operating the 2 nd valve by the fluid pressure of the compressive fluid.
Description
Technical Field
The present invention relates to a reciprocating compressor-expander suitable for compressing or expanding a compressible fluid, for example.
Background
As renewable energy sources, photovoltaic power generation apparatuses, wind power generation apparatuses, and the like have been widely used from the past. However, in a power generation device using such natural energy, the amount of power generation fluctuates greatly, and it is sometimes difficult to effectively use the power according to the power demand.
The reason for this is that: when power generation is performed using natural energy that cannot be controlled manually, the amount of power generation may greatly exceed the required power, and excessive surplus power may be generated, and therefore, in the worst case, a power interruption phenomenon may occur. Therefore, in order to prevent such excessive surplus power from being generated, a power generation device using natural energy may block a part of its power.
As a measure against this excessive surplus power, it is conceivable to temporarily store surplus power in a storage battery, discharge the surplus power when the power demand increases, and supply power to the grid, thereby achieving power balance. This storage method using a storage battery is preferable in terms of utilization and the like because it directly stores electric energy, but the storage battery is an extremely expensive energy storage device because it requires the use of special metals and the like.
As another solution for saving surplus power based on natural energy, it is considered to convert electric energy into compressed air energy for storage. With regard to this electricity storage method, a test plant of an energy storage device that converts energy into compressed air energy has been constructed, and a verification experiment has also been completed.
In this method, a motor is operated using surplus electric power, a compressor is rotationally driven by the motor to generate compressed air, the compressed air is stored in a temporary storage tank, and when the electric power is insufficient, an expander is rotationally driven by the compressed air to generate electric power, and the electric power is converted into electric power again. According to a verification experiment, the comprehensive efficiency of the method is confirmed to reach 60-70%. In this energy storage device, a screw compressor is used as a compression-expansion machine.
On the other hand, there are other reciprocating compressors using pistons. This conventional reciprocating compressor using a piston operates a suction valve and a discharge valve only by a simple elastic force generated by a plate spring or the like (see patent document 1).
However, the conventional screw compressor has the following problem of concern. That is, a certain gap is necessarily formed between the male and female rotors and between the rotors and the casing in the structure of the screw compressor, and a compressed object leaks through the gap during compression, thereby reducing compression efficiency and expansion efficiency.
In addition, when both the compression stroke and the expansion stroke are performed by one compression-expansion machine, the rotation direction of the compression-expansion machine is opposite in each stroke. Therefore, in order to simplify the electric power equipment by rotating the electric motor for compression and the generator for power generation in the same direction, some kind of switching device or the like is required.
In addition, the screw compressor has a relatively small capacity and is not suitable for a large capacity energy storage device. Further, the screw compressor cannot adjust the capacity by the compressor-expander alone, and requires a pressure adjusting device for compressing air. Further, in order to solve such a problem, a converter such as an inverter is required for the power system, and in this case, the price of the device itself becomes high.
On the other hand, in the conventional reciprocating compressor, as described above, the suction valve and the discharge valve are operated by the spring such as the plate spring, and in this case, the suction valve and the discharge valve are operated only by the elastic force set in advance in accordance with the differential pressure with the internal pressure, and there is a problem that it is inevitably difficult to arbitrarily and appropriately adjust the suction flow rate and the discharge flow rate. In addition, there is a problem that the expander cannot be used as the expander as well.
Accordingly, the present inventors have developed a new reciprocating compressor-expander which is extremely efficient in compression and expansion, has the same rotation direction, has a large capacity, is suitable for use in a large-capacity power storage device or the like, has an extremely simple capacity adjustment, and does not require a converter such as an inverter in a power system when used in the power storage device, and have filed the application in japanese patent application No. 2019-227516.
[ background Art document ]
[ patent document ]
[ patent document 1] Japanese patent laid-open No. Hei 2-130278
Disclosure of Invention
[ problems to be solved by the invention ]
In the reciprocating compressor-expander proposed by the present inventors, the suction valve for sucking the compressible fluid and the discharge valve for discharging the compressible fluid are configured to be closed by an air spring, for example. The elastic force of the air spring is determined by considering an inertial force generated by the weight and acceleration of the operating portion, a sealing property for preventing the valve sealing portion from leaking fluid, a differential pressure acting on the valve umbrella portion when the valve is opened, and the like.
On the other hand, in the internal combustion engine, for example, the differential pressure applied to the valve umbrella portion of the umbrella valve is about 1bar at most, but in the reciprocating compressor-expander for compressing the compressible fluid to a high pressure or expanding the compressible fluid at a high pressure, the differential pressure may be as high as about 10 times that of the internal combustion engine at a moment when the valve is opened in the reciprocating compressor-expander. Therefore, in order to reliably close the valve, it is necessary to, for example, strengthen the spring force of the air spring.
The internal pressure of the cylinder becomes extremely high particularly at the time of compression, and the valve umbrella portion of the discharge valve is pushed from the inside of the cylinder to the valve closing side by a strong force. Therefore, since the air spring has a strong elastic force, a large urging force is required to open the discharge valve during compression. However, it is estimated from the solid line portion in fig. 6 that when the discharge valve is opened, the differential pressure applied to the valve umbrella portion of the discharge valve due to the flow of the compressible fluid is rapidly reduced.
As described above, the reciprocating type compressor-expander for compressing or expanding a compressible fluid has the following problems: in order to reliably close the valve, the spring force of the air spring needs to be further increased, and the spring force of the air spring is increased, so that a large driving force is required for the hydraulically driven or electrically driven valve driving mechanism for opening the valve. In addition, there are problems as follows: as described above, the internal pressure of the cylinder becomes extremely high particularly at the time of compression, which causes the valve closing side to be pushed toward the valve closing side, and at the moment of opening, a larger driving force is required for the hydraulically driven or electrically driven valve driving mechanism for opening the valve.
To obtain such a large driving force, a method of opening the valve by a cam drive method may be employed, but the cam drive method has a problem that the device is generally large in size. In the case of the hydraulically driven or electrically driven valve drive mechanism proposed by the present inventor, it is necessary to supply a high hydraulic pressure to the hydraulic cylinder only for a moment when the valve is opened, and there is a concern that, for example, the hydraulic pressure source is increased in pressure and a special hydraulic pressure booster is required. Further, since the differential pressure applied to the valve umbrella portion changes in accordance with the load of the reciprocating compressor-expander, it is necessary to control the pressure of the hydraulic source in accordance with the load, and this problem is also feared.
The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a reciprocating compressor-expander which can eliminate the increase in size of the device, can resist a strong spring force for closing the valve, and can easily open the valve with a low urging force by a simple mechanism in accordance with the load of the reciprocating compressor-expander.
[ means for solving problems ]
In order to solve the above problem, a reciprocating compressor-expander according to the present invention includes: a main body piston sliding in the main body cylinder; a crankshaft connected to the main piston to rotate; a 1 st valve and a 2 nd valve, wherein the 1 st valve is opened to suck the low-pressure compressible fluid into the main cylinder from the low pressure path, the compressible fluid sucked from the 1 st valve is compressed to be high-pressure by the action of the main piston, the 2 nd valve is opened to discharge the compressible fluid to the high pressure path, or the 2 nd valve is opened to flow the high-pressure compressible fluid into the main cylinder from the high pressure path, the compressible fluid flowing from the 2 nd valve is expanded to be low-pressure by the action of the main piston, and the 1 st valve is opened to discharge the compressible fluid to the low pressure path; a 1 st valve driving mechanism driven by oil pressure or electricity to drive the 1 st valve and the 2 nd valve; and a 2 nd valve drive mechanism for operating the 2 nd valve by the fluid pressure of the compressible fluid.
In this way, by further providing the 2 nd valve driving mechanism which operates the 2 nd valve by the fluid pressure of the compressible fluid, the 2 nd valve can be easily opened without particularly increasing the driving force of the 1 st valve driving mechanism which is hydraulically driven or electrically driven.
In the reciprocating compressor-expander, the 2 nd valve driving mechanism preferably includes a fluid pressure piston connected to the 2 nd valve, and the 2 nd valve is operated by applying a fluid pressure of the compressible fluid to a piston surface.
In this way, the 2 nd valve drive mechanism includes the fluid pressure piston connected to the 2 nd valve, and the 2 nd valve is operated by applying the fluid pressure of the compressive fluid to the piston surface, whereby the 2 nd valve drive mechanism operated by the fluid pressure of the compressive fluid can be easily formed. In addition, the method has the great advantage that no external energy source such as oil pressure or electricity is needed.
In the reciprocating compression-expansion engine, it is preferable that the fluid pressure of the compressible fluid in the high pressure passage is applied to the 1 st piston surface on the 2 nd valve side of the piston surface by the fluid pressure piston.
In this way, by applying the fluid pressure of the compressible fluid in the high pressure passage of the reciprocating compressor-expander to the 1 st piston surface on the 2 nd valve side of the fluid pressure piston, the pressing force generated by the fluid pressure of the compressible fluid is applied to the 1 st piston surface on the 2 nd valve side of the fluid pressure piston, and the pressing force generated by the fluid pressure of the compressible fluid from the high pressure side is applied to the 2 nd valve, and these pressing forces are offset by the amount, so that the fluid pressure of the compressible fluid in the high pressure passage is less likely to be affected by the valve opening operation of the 2 nd valve during both compression and expansion. That is, in all operating states of the reciprocating compressor-expander, it is not necessary to increase the urging force of the hydraulically driven or electrically driven 1 st valve driving mechanism toward the 2 nd valve opening side in particular only for opening the 2 nd valve.
In the reciprocating compression-expansion machine, preferably, a fluid pressure cylinder having a high-pressure fluid communication passage for communicating the 1 st cylinder chamber on the 2 nd valve side with the high-pressure passage slides a fluid pressure piston inside the fluid pressure cylinder.
In this way, the fluid pressure cylinder having the high-pressure fluid communication passage for communicating the 1 st cylinder chamber on the 2 nd valve side with the high pressure passage of the reciprocating type compression-expansion engine slides the fluid pressure piston therein, and thereby the pressing force generated by the fluid pressure of the compressible fluid is applied to the 1 st piston surface on the 2 nd valve side of the fluid pressure piston, and the pressing force generated by the fluid pressure of the compressible fluid from the high pressure passage side is applied to the 2 nd valve, and the pressing forces are offset by the pressing forces, so that the fluid pressure of the compressible fluid in the high pressure passage is less likely to be affected by the fluid pressure in the valve opening operation of the 2 nd valve, both at the time of compression and at the time of expansion. That is, in all operating states of the reciprocating compressor-expander, it is not necessary to increase the urging force of the hydraulically driven or electrically driven 1 st valve driving mechanism toward the 2 nd valve opening side in particular only for opening the 2 nd valve.
In the reciprocating compressor-expander, preferably, the outer diameter of the fluid pressure piston on the 2 nd valve side is formed substantially the same as the outer diameter of an exposed surface on which the 2 nd valve is exposed on the high pressure side when the 2 nd valve is closed.
In this way, the outer diameter of the 2 nd valve side of the fluid pressure piston is formed to be substantially the same as the outer diameter of the exposed surface exposed on the high pressure side of the 2 nd valve when the 2 nd valve is closed, and therefore, the pressing force generated by the fluid pressure of the compressive fluid is applied to the 1 st piston surface on the 2 nd valve side of the fluid pressure piston, and the pressing force generated by the fluid pressure of the compressive fluid from the high pressure side is applied to the 2 nd valve, and these pressing forces are substantially cancelled out, so that the influence of the fluid pressure of the compressive fluid in the high pressure side in the valve opening operation of the 2 nd valve is not easily exerted either at the time of compression or expansion. That is, in all operating states of the reciprocating compressor-expander, it is not necessary to increase the urging force of the hydraulically driven or electrically driven 1 st valve driving mechanism toward the 2 nd valve opening side in particular only for opening the 2 nd valve.
In the reciprocating compressor-expander, the high-pressure fluid communication passage preferably extends toward the high-pressure side so that the inner diameter of the fluid pressure cylinder is substantially constant.
In this way, the high-pressure fluid communication passage is formed so as to extend toward the high-pressure passage side with the inner diameter of the fluid pressure cylinder being substantially constant, and the high-pressure fluid communication passage is easily formed by using the fluid pressure cylinder as the high-pressure fluid communication passage. Further, since the inner diameter does not change, the fluid pressure of the compressible fluid in the high-pressure passage can be prevented from being reduced when applied to the fluid pressure cylinder.
In the reciprocating compressor-expander, the fluid pressure of the compressible fluid in the main cylinder is preferably applied to the 2 nd piston surface on the opposite side of the 2 nd valve by the fluid pressure piston.
In this way, by applying the fluid pressure of the compressible fluid in the main cylinder of the reciprocating compressor-expander to the 2 nd piston surface on the opposite side of the 2 nd valve of the fluid pressure piston, the pressing force toward the 2 nd valve opening side by the fluid pressure of the compressible fluid is applied to the 2 nd piston surface, and the pressing force toward the 2 nd valve closing side by the fluid pressure of the compressible fluid in the main cylinder is applied to the 2 nd valve surface, and these pressing forces are cancelled out by the action of the fluid pressure piston, and even if, for example, a very high fluid pressure of the compressible fluid acts in the main cylinder at the time of compression, it is not necessary to particularly increase the urging force toward the 2 nd valve opening side by the 1 st valve driving mechanism that is hydraulically or electrically driven only for opening the 2 nd valve.
On the other hand, for example, when the fluid pressure of the compressible fluid in the main cylinder of the reciprocating compressor-expander during expansion is low, the pressure applied to the 1 st piston surface on the opposite side of the 2 nd valve of the fluid pressure piston is also reduced, and therefore the pressing force applied to the fluid pressure piston is automatically and appropriately adjusted in all operating states of the reciprocating compressor-expander.
In the reciprocating compression-expansion machine, preferably, the fluid pressure cylinder is provided with a cylinder communication passage for communicating the 2 nd cylinder chamber on the opposite side of the 2 nd valve with the inside of the main cylinder so as to slide the fluid pressure piston therein.
In this way, the fluid pressure cylinder having the cylinder communication passage slides the fluid pressure piston inside, the cylinder communication passage communicates the 2 nd cylinder chamber on the opposite side of the 2 nd valve with the inside of the main cylinder, whereby the 2 nd piston surface on the opposite side of the 2 nd valve of the fluid pressure piston is applied with a pressing force toward the 2 nd valve opening side by the fluid pressure of the compressive fluid, the 2 nd valve is applied with a pressing force toward the 2 nd valve closing side by the fluid pressure of the compressive fluid in the main cylinder, the pressing forces are cancelled out by the action of the fluid pressure piston, for example, even if a very high fluid pressure of the compressible fluid acts on the main cylinder during compression, it is not necessary to increase the urging force of the hydraulically driven or electrically driven 1 st valve driving mechanism toward the 2 nd valve opening side only for opening the 2 nd valve.
On the other hand, for example, when the fluid pressure of the compressible fluid in the main cylinder is low during expansion, the pressure applied to the 2 nd piston surface on the opposite side of the 2 nd valve of the fluid pressure piston is also reduced, and therefore the pressing force applied to the fluid pressure piston is automatically and appropriately adjusted in all operating states of the reciprocating compressor-expander.
[ Effect of the invention ]
As described above, the reciprocating compressor-expander according to the present invention includes: a main body piston sliding in the main body cylinder; a crankshaft connected to the main piston to rotate; a 1 st valve and a 2 nd valve, wherein the 1 st valve is opened to suck the low-pressure compressible fluid into the main cylinder from the low pressure path, the compressible fluid sucked from the 1 st valve is compressed to be high-pressure by the action of the main piston, the 2 nd valve is opened to discharge the compressible fluid to the high pressure path, or the 2 nd valve is opened to flow the high-pressure compressible fluid into the main cylinder from the high pressure path, the compressible fluid flowing from the 2 nd valve is expanded to be low-pressure by the action of the main piston, and the 1 st valve is opened to discharge the compressible fluid to the low pressure path; a hydraulically or electrically driven valve drive mechanism for operating the 1 st and 2 nd valves; and a 2 nd valve drive mechanism for operating the 2 nd valve by the fluid pressure of the compressible fluid.
Therefore, the following excellent effects are exhibited: the valve can be easily opened with a simple mechanism by a low urging force in response to the load of the reciprocating type compression-expansion machine while suppressing the increase in size of the device and resisting a strong urging force for closing the valve.
Drawings
Fig. 1 is a schematic view showing a reciprocating compressor-expander.
Fig. 2 is a schematic diagram showing a hydraulically driven valve driving mechanism of the reciprocating compressor-expander of fig. 1.
Fig. 3 is a partial longitudinal cross-sectional view showing details of the reciprocating compressor-expander of the present invention.
Fig. 4 is a graph showing a relationship between a crank angle and an air pressure in the main cylinder in the reciprocating compressor-expander of fig. 3.
Fig. 5 is a graph showing a relationship between a crank angle and an air pressure in the main cylinder at the time of expansion in the reciprocating compressor-expander of fig. 3.
Fig. 6 is a graph showing a relationship between a crank angle and an operating oil pressure required for the hydraulic cylinder in the reciprocating compressor-expander of fig. 3.
Fig. 7 is a partial longitudinal cross-sectional view showing another form of the balance piston of fig. 3.
Detailed Description
The mode of the reciprocating compressor-expander for carrying out the present invention will be described in detail with reference to fig. 1 to 7.
As shown in fig. 1, the reciprocating compressor-expander 1 includes: a main body piston 3 sliding hermetically in the main body cylinder 2; and a crankshaft 5 connected to the main piston 3 via a connecting rod 4 and rotating. And has: an intake valve (1 st valve) 7 for taking low-pressure air (compressible fluid) into the main cylinder from the outside during a compression stroke (compression); and a discharge valve (2 nd valve) 8 for discharging compressed air to the outside through a high-pressure air passage (high-pressure passage) 9 described later, the compressed air being sucked from the suction valve 7 and compressed by the operation of the main body piston 3 to become high pressure.
In the expansion stroke (expansion time) of the reciprocating compressor-expander 1, the discharge valve 8 is opened to allow high-pressure compressed air to flow from the outside into the main cylinder 2 through the high-pressure air passage 9, while the intake valve 7 is opened to discharge air to the outside, and the air flows in from the discharge valve 8 and expands to a low pressure by the operation of the main piston 3.
As shown in fig. 2, an air spring 11 that constantly biases the intake valve 7 toward the valve closing side is disposed on the valve shaft 7a of the intake valve 7. The hydraulic cylinder 12 is directly connected to the valve shaft 7a of the intake valve 7 via an air spring 11. That is, when hydraulic pressure is applied to the hydraulic cylinder 12, the hydraulic cylinder 12 opens the suction valve 7 against the biasing force of the air spring 11.
A hydraulic actuator 13 is disposed on the upstream side of the hydraulic cylinder 12, and the operation of the hydraulic actuator 13 is controlled by an electronic control valve 25. The controller 20 electrically controls the operation of the electronic control valve 25. The hydraulic pressure is supplied to the electronic control valve 25 from the inlet hydraulic main pipe 14, and is discharged from the outlet hydraulic main pipe 15.
Similarly to the intake valve 7, the discharge valve 8 is also provided with an air spring 11, a hydraulic cylinder 12, and the like in this order toward the upstream side of the valve drive mechanism, and the intake valve 7 and the discharge valve 8 are operated independently of each other under the control of the controller 20. That is, in the valve driving mechanism, the suction valve 7 and the discharge valve 8 are opened and closed independently of each other. However, the program in the controller 20 may associate both of them in some manner and operate them.
As described above, the hydraulic cylinder 12 is connected to the valve shaft 7a of the intake valve 7 and the valve shaft 8a of the discharge valve 8, respectively, and directly opens the intake valve 7 and the discharge valve 8, respectively. Therefore, the opening and closing operations of the suction valve 7 and the discharge valve 8 can be performed very quickly and reliably in response to the instruction from the controller 20. The air spring 11, the hydraulic cylinder 12, the hydraulic actuator 13, the electronic control valve 25, and the controller 20 form a hydraulically driven valve drive mechanism (the 1 st valve drive mechanism).
A crank angle detection sensor, not shown, for detecting the rotation angle of the crankshaft 5, a compressed air tank internal pressure detection sensor, not shown, for detecting the air pressure of compressed air in the high-pressure air passage 9, an external compressed air tank, and the like, an electric force detection sensor, not shown, for detecting the rotational power of an external generator, not shown, connected to the crankshaft 5 and driven in rotation thereof, and the like are electrically connected to the controller 20, and the controller 20 controls the operation of the electronic control valve 25 based on the parameters detected by these sensors, and causes the suction valve 7 and the discharge valve 8 of the reciprocating compressor-expander 1 to open and close independently of each other via the hydraulic actuator 13 and the hydraulic cylinder 12.
As shown in fig. 2, when the suction valve 7 or the discharge valve 8 of the reciprocating compressor-expander 1 is closed, the hydraulic actuator 13 does not supply the hydraulic pressure to the hydraulic cylinder 12, and therefore the suction valve 7 or the discharge valve 8 is closed by the biasing force of the air spring 11. When the controller 20 electrically sends an instruction to open the valve to the electronic control valve 25, the electronic control valve 25 operates the hydraulic actuator 13 by the hydraulic pressure supplied from the inlet hydraulic main pipe 14 to supply the hydraulic pressure to the hydraulic cylinder 12. Thereby, the suction valve 7 or the discharge valve 8 is opened against the biasing force of the air spring 11.
When the controller 20 electrically sends an instruction to close the valve to the electronic control valve 25, the electronic control valve 25 operates the hydraulic actuator 13 to block the supply of the hydraulic pressure to the hydraulic cylinder 12 and release the hydraulic pressure. Thereby, the suction valve 7 or the discharge valve 8 is closed by the biasing force of the air spring 11. The oil pressure is discharged from the outlet oil pressure main 15.
In the compression stroke of the reciprocating compressor-expander 1, the controller 20 opens the intake valve 7 to take in low-pressure air, reciprocates the main piston 3 through the crankshaft by an external motor or the like, adiabatically compresses the taken-in air by the main piston 3, increases the pressure and temperature of the air in the main cylinder 2, opens the discharge valve 8, discharges the compressed air through the high-pressure air passage 9, and supplies the compressed air to an external compressed air tank or the like, not shown.
This makes it possible to convert surplus electric power into compressed air energy once and store the compressed air energy in an external compressed air tank or the like, and also makes it possible to adjust the rotational power of the external motor by the controller 20 on the valve drive mechanism side, thereby making it possible to simplify electric control on the motor side.
In the expansion stroke of the reciprocating compressor-expander 1, the controller 20 opens the discharge valve 8 to allow high-pressure air to flow from the outside through the high-pressure air passage 9, operates the main body piston 3 by the air pressure to adiabatically expand the air that flows in, lowers the pressure and temperature of the air in the main body cylinder 2, and then opens the suction valve 7 to discharge the air having the lowered pressure and temperature to the outside. Further, power can be generated by an external generator or the like connected to and rotationally driven by the crankshaft 5 via the crankshaft 5 rotationally driven by the main body piston 3.
This enables, for example, excess electric power to be converted into compressed air energy, to be temporarily stored in an external compressed air tank or the like, and the stored pressure energy of the air to be regenerated into electric power when necessary. In addition, the rotational power of the external generator can be adjusted by the controller 20 on the 1 st valve drive mechanism side, and the electric control on the generator side can be simplified.
As shown in fig. 2 and 3, in the reciprocating compressor-expander 1, a circular flat plate-shaped balance piston (2 nd valve driving mechanism, fluid pressure piston) 17 is disposed on a valve shaft 8a between a valve umbrella portion 8b of the discharge valve 8 as an umbrella-shaped valve and the air spring 11.
As shown in fig. 3, the balance piston cylinder (2 nd valve drive mechanism, fluid pressure cylinder, high-pressure fluid communication passage) 18 slides the balance piston 17 inside, the valve umbrella portion 8b side (2 nd valve side) of the discharge valve 8 of the balance piston cylinder 18 opens on the entire surface in the high-pressure air passage 9 extending from the discharge valve 8 to the outside, and the pressure (fluid pressure) P1 of the compressed air in the high-pressure air passage 9 is applied to the 1 st piston surface 17a on the valve umbrella portion 8b side of the balance piston 17.
Further, the balance piston cylinder 18 projects toward the valve umbrella portion 8b so that the inner diameter thereof is constant, and continues to the high-pressure air passage 9, thereby forming a 1 st cylinder chamber 18a on the valve umbrella portion 8b side. The balance piston cylinder is formed to extend toward the high-pressure air passage 9 so that the inner diameter thereof is substantially constant.
That is, in the reciprocating compressor-expander 1, the balance piston cylinder 18 slides the balance piston 17 therein, the balance piston cylinder 18 communicates between the 1 st cylinder chamber 18a and the high-pressure air passage 9 extending from the discharge valve 8 to the outside via the balance piston cylinder 18, and the outer diameter of the balance piston 17 on the valve umbrella portion 8b side or the inner diameter of the balance piston cylinder 18 on the valve umbrella portion 8b side is formed to be substantially the same as the outer diameter of the exposed surface 8c, which is the surface where the discharge valve 8 is exposed in the high-pressure air passage 9 in the closed state of the discharge valve 8.
The operation force of the balance piston 17 is affected by the ratio of the air pressure effective area S2 to the air pressure effective area S3, and the like, and the air pressure effective area S2 is an area where the exposed surface 8c of the discharge valve 8 on the high-pressure air passage 9 side effectively receives the air pressure in the closed state, and the air pressure effective area S3 is an area where the 1 st piston surface 17a on the valve umbrella portion 8b side of the balance piston 17 effectively receives the air pressure.
However, the reciprocating compressor-expander 1 is formed in the following shape as described above: since the pressure of the compressed air in the high-pressure air passage 9 applied to the 1 st piston surface 17a of the balance piston 17 is not reduced as much as possible, even if the compressed air in the high-pressure air passage 9 is a compressible fluid, the pressing force generated by the pressure P2 of the compressed air on the high-pressure air passage 9 side applied to the discharge valve 8 and the pressing force generated by the pressure P3 of the compressed air applied to the 1 st piston surface 17a of the balance piston 17 can be almost cancelled out, and the pressure of the compressed air in the high-pressure air passage 9 in the valve opening operation of the discharge valve 8 is not easily affected by the pressure of the compressed air in the high-pressure air passage 9 in both the compression and expansion.
That is, in all operating states of the reciprocating compressor-expander 1, it is not necessary to increase the urging force of the hydraulic cylinder 12 for urging the discharge valve 8 toward the valve opening side. Further, in order to reliably close the discharge valve 8 when the air pressure in the main cylinder 2 is low, it is necessary to increase the elastic force of the air spring 11, and the pressing force generated by the pressure P3 of the compressed air is applied to the 1 st piston surface 17a of the balance piston 17, and the elastic force of the air spring 11 can be weakened by the pressing force.
On the other hand, the air spring 11 side (the side opposite to the 2 nd valve) of the balance piston cylinder 18, that is, the side opposite to the 1 st piston chamber 18a is a 2 nd cylinder chamber 18b, a pressure supply passage (cylinder communication passage) 19 is provided between the 2 nd cylinder chamber 18b and the inside of the main cylinder 2, and the 2 nd cylinder chamber 18b of the balance piston cylinder 18 and the inside of the main cylinder 2 communicate with each other through the pressure supply passage 19.
That is, the compressed air in the main cylinder 2 is supplied to the 2 nd cylinder chamber 18b of the balance piston cylinder 18, the 2 nd piston surface 17b is provided on the air spring 11 side of the balance piston 17, that is, on the opposite side of the 1 st piston surface 17a, and a pressure P4 close to the pressure (fluid pressure) P1 of the compressed air in the main cylinder 2 is applied to the 2 nd piston surface 17 b.
Therefore, the 2 nd piston surface 17b of the balance piston 17 is applied with the pressing force by the pressure of the compressed air, the discharge valve 8 is applied with the pressing force by the pressure of the compressed air on the main cylinder 2 side, and both the pressing forces are cancelled out by each other, so that the pressure of the compressed air in the main cylinder 2 is not easily affected by the valve opening operation of the discharge valve 8 at the time of compression or expansion.
The pressure P4 in the 2 nd cylinder chamber 18b of the balance piston cylinder 18 changes as appropriate in accordance with the fluctuation in the pressure P1 of the compressed air on the main cylinder 2 side to which the discharge valve 8 is applied. That is, in all the operating states of the reciprocating compressor-expander 1, there is no need to increase the urging force of the hydraulic cylinder 12 for urging the discharge valve 8 toward the valve opening side.
Since the air, which is the object to be compressed and expanded in the reciprocating compressor-expander 1, is a compressible fluid, it is affected by the cross-sectional area, length, shape, and the like of the pressure supply passage 19, and the pressure P1 of the compressed air on the main cylinder 2 side of the reciprocating compressor-expander 1 to which the discharge valve 8 is applied is not necessarily the same as the pressure P4 in the 2 nd cylinder chamber 18b of the balance piston cylinder 18 in all operating states of the reciprocating compressor-expander 1.
Further, the ratio of the air pressure effective area S1 to the air pressure effective area S4 is different, and the like, and the influence on the urging force of the hydraulic cylinder 12 with respect to the discharge valve 8 is different. The air pressure effective area S1 is an area for effectively receiving the air pressure at the end surface of the valve umbrella portion 8b of the discharge valve 8 on the main cylinder 2 side, and the air pressure effective area S4 is an area for effectively receiving the air pressure at the 2 nd piston surface 17b of the balance piston 17.
Fig. 4 is a graph showing the relationship between the crank angle at the time of compression in the reciprocating compressor-expander 1 and the air pressure in the main cylinder 2, and fig. 5 is a graph showing the relationship between the crank angle at the time of expansion in the reciprocating compressor-expander 1 and the air pressure in the main cylinder 2. As shown in fig. 4 and 5, the pressure P1 of the compressed air in the main cylinder 2 of the reciprocating compressor-expander 1 greatly varies with the crank angle, but becomes almost the highest pressure when the discharge valve 8 is opened both at the time of compression and at the time of expansion.
In fig. 6, a solid line shows a relationship between a crank angle and an operating pressure of the hydraulic cylinder required when the discharge valve is opened in the conventional reciprocating compressor-expander, a broken line shows a relationship between a crank angle and an operating pressure of the hydraulic cylinder 12 required when the discharge valve 8 is opened in the reciprocating compressor-expander 1, and a two-dot chain line shows an open/close valve state of the discharge valve 8 with respect to the crank angle.
As shown in fig. 6, in the reciprocating compressor-expander 1, the operating pressure of the hydraulic cylinder 12 required when the discharge valve 8 is opened is significantly lower than that of the conventional reciprocating compressor-expander, and is almost close to the operating pressure of the hydraulic cylinder 12 after the valve is opened.
As shown in fig. 7, in order to change the ratio of the air pressure effective area of the 1 st piston surface 27a on the valve umbrella side (2 nd valve side) of the balance piston 27 to the 2 nd piston surface 27b on the air spring side, for example, a balance piston 27 with a step may be used. Accordingly, the pneumatic effective areas S3 and S4 can be changed, and the operating pressure required for the hydraulic cylinder 12 of the reciprocating compressor-expander 1 can be adjusted.
As described above, the reciprocating compressor-expander 1 includes: an intake valve 7 and a discharge valve 8, the intake valve 7 being opened to draw low-pressure compressed air into the main cylinder 2 from the outside, the compressed air drawn in from the intake valve 7 being compressed to be high-pressure by the operation of the main piston 3, the discharge valve 8 being opened to discharge the compressed air to the high-pressure air passage 9, or the discharge valve 8 being opened to draw high-pressure compressed air into the main cylinder 2 from the high-pressure air passage 9, the compressed air drawn in from the discharge valve 8 being expanded to be low-pressure by the operation of the main piston 3, the intake valve 7 being opened to discharge the compressed air to the outside; hydraulically or electrically driven valve driving mechanisms 12, 13, 20, and 25 for operating the suction valve 7 and the discharge valve 8; and a balance piston 17 and a balance piston cylinder 18 for operating the discharge valve 8 by the pressure of the compressed air, so that the discharge valve 8 can be easily opened with a low urging force by a simple mechanism against the strong elastic force of the air spring 11 for closing the valve while eliminating the increase in size of the device and in accordance with the load of the reciprocating type compressor-expander 1.
The reciprocating compressor-expander 1 is merely an example, and various changes can be made based on the gist of the present invention, and they are not excluded from the scope of the present invention.
[ description of symbols ]
1 reciprocating type compression-expansion machine
2 main body cylinder
3 main body piston
4 connecting rod
5 crankshaft
7 suction valve (1 st valve)
7a valve shaft
8 blow-off valve (No. 2 valve)
8a valve shaft
8b valve umbrella part
8c exposed surface
9 high pressure air circuit (high road roller)
11 air spring
12 oil pressure cylinder (1 st valve driving mechanism)
13 oil pressure actuator (1 st valve driving mechanism)
14 inlet oil pressure main pipe
15 outlet oil pressure main pipe
17 balance piston (2 nd valve driving mechanism, fluid pressure piston)
18 balance piston cylinder (2 nd valve driving mechanism, fluid pressure cylinder, high pressure fluid communication path)
19 pressure supply path (Cylinder communicating path)
20 controller (1 st valve driving mechanism)
25 electronic control valve (1 st valve driving mechanism)
27 balance piston with step difference (2 nd valve driving mechanism, fluid pressure piston)
P1, P2, P3, P4 pressures (fluid pressures)
S1, S2, S3, S4 air pressure effective area.
Claims (3)
1. A reciprocating type compression-expansion machine is characterized by comprising: a main body piston (3) sliding in the main body cylinder (2); a crankshaft (5) connected to the main body piston to rotate; a 1 st valve (7) and a 2 nd valve (8), wherein the 1 st valve (7) sucks a low-pressure compressible fluid into the main cylinder from a low pressure path after opening, compresses the compressible fluid sucked from the 1 st valve by the operation of the main piston to a high pressure, and the 2 nd valve (8) discharges the compressible fluid to a high pressure path after opening, or the 2 nd valve (8) flows a high-pressure compressible fluid into the main cylinder from a high pressure path after opening, expands the compressible fluid flowing from the 2 nd valve to a low pressure by the operation of the main piston, and the 1 st valve (7) discharges the compressible fluid to a low pressure path after opening; a 1 st hydraulically or electrically driven valve drive mechanism (12, 13, 20, 25) for operating the 1 st valve and the 2 nd valve; and a fluid pressure piston (17) connected to the 2 nd valve, and the 2 nd valve is operated by applying a fluid pressure of the compressive fluid to the 1 st and 2 nd piston surfaces (17a, 17b) on both sides.
2. A reciprocating type compression-expansion machine is characterized by comprising: a main body piston (3) sliding in the main body cylinder (2); a crankshaft (5) connected to the main body piston to rotate; a 1 st valve (7) and a 2 nd valve (8), wherein the 1 st valve (7) sucks a low-pressure compressible fluid into the main cylinder from a low pressure path after opening, compresses the compressible fluid sucked from the 1 st valve by the operation of the main piston to a high pressure, and the 2 nd valve (8) discharges the compressible fluid to a high pressure path after opening, or the 2 nd valve (8) flows a high-pressure compressible fluid into the main cylinder from a high pressure path after opening, expands the compressible fluid flowing from the 2 nd valve to a low pressure by the operation of the main piston, and the 1 st valve (7) discharges the compressible fluid to a low pressure path after opening; a 1 st hydraulically or electrically driven valve drive mechanism (12, 13, 20, 25) for operating the 1 st valve and the 2 nd valve; and a fluid pressure piston (17) connected to the 2 nd valve, and configured to operate the 2 nd valve by applying a fluid pressure of the compressive fluid to piston surfaces (17a, 17 b); the fluid pressure piston is applied with the fluid pressure of the compressive fluid in the main cylinder on a 2 nd piston surface (17b) on the opposite side of the 2 nd valve (8).
3. A reciprocating type compression-expansion machine is characterized by comprising: a main body piston (3) sliding in the main body cylinder (2); a crankshaft (5) connected to the main body piston to rotate; a 1 st valve (7) and a 2 nd valve (8), wherein the 1 st valve (7) sucks a low-pressure compressible fluid into the main cylinder from a low pressure path after opening, compresses the compressible fluid sucked from the 1 st valve by the operation of the main piston to a high pressure, and the 2 nd valve (8) discharges the compressible fluid to a high pressure path after opening, or the 2 nd valve (8) flows a high-pressure compressible fluid into the main cylinder from a high pressure path after opening, expands the compressible fluid flowing from the 2 nd valve to a low pressure by the operation of the main piston, and the 1 st valve (7) discharges the compressible fluid to a low pressure path after opening; a 1 st hydraulically or electrically driven valve drive mechanism (12, 13, 20, 25) for operating the 1 st valve and the 2 nd valve; and a fluid pressure piston (17) connected to the 2 nd valve, and configured to operate the 2 nd valve by applying a fluid pressure of the compressive fluid to piston surfaces (17a, 17 b); a fluid pressure cylinder (18) slides the fluid pressure piston in the interior thereof, the fluid pressure cylinder (18) further comprising a cylinder communication passage (19), the cylinder communication passage (19) communicating a 2 nd cylinder chamber (18b) on the opposite side of the 2 nd valve with the inside of the main body cylinder.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019232172A JP6812532B1 (en) | 2019-12-24 | 2019-12-24 | Reciprocating compression expander |
| JP2019-232172 | 2019-12-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112648168A true CN112648168A (en) | 2021-04-13 |
| CN112648168B CN112648168B (en) | 2022-03-08 |
Family
ID=74096406
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011555685.8A Active CN112648168B (en) | 2019-12-24 | 2020-12-24 | Reciprocating compression expander |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6812532B1 (en) |
| CN (1) | CN112648168B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2018121684A (en) * | 2017-01-30 | 2018-08-09 | 株式会社三洋物産 | Game machine |
| JP7267633B2 (en) * | 2021-09-27 | 2023-05-02 | 株式会社サクション瓦斯機関製作所 | Compressor and expander |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB127993A (en) * | 1918-06-12 | 1919-06-12 | Seward Seymoure Vernon | Improvements in and relating to Compressed Air Power Plant. |
| JPS5930575U (en) * | 1982-08-23 | 1984-02-25 | いすゞ自動車株式会社 | Air compressor intake air blowback prevention device |
| EP0921309A1 (en) * | 1997-12-02 | 1999-06-09 | Poclain Hydraulics | Hydraulic motor with switch valve |
| JP2001303995A (en) * | 2000-04-26 | 2001-10-31 | Toyota Motor Corp | Internal combustion engine |
| US20110083434A1 (en) * | 2007-03-07 | 2011-04-14 | Thermal Power Recovery Llc | Method and Apparatus For Achieving Higher Thermal Efficiency In A Steam Engine or Steam Expander |
| CN102209836A (en) * | 2008-11-10 | 2011-10-05 | 河锡奉 | Cylinder driving apparatus using air pressure |
| CN102725532A (en) * | 2010-01-29 | 2012-10-10 | Ulvac机工株式会社 | Pump |
| CN102787866A (en) * | 2012-08-17 | 2012-11-21 | 彭学军 | Turbine engine using compressed air as working energy |
| CN104454014A (en) * | 2014-10-21 | 2015-03-25 | 大连理工大学 | Compressed air engine-air compressor integrated dual-purpose machine |
| CN106460514A (en) * | 2014-04-04 | 2017-02-22 | Z机械技术研究所有限公司 | Expander and air-freezing apparatus equipped with same |
-
2019
- 2019-12-24 JP JP2019232172A patent/JP6812532B1/en active Active
-
2020
- 2020-12-24 CN CN202011555685.8A patent/CN112648168B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB127993A (en) * | 1918-06-12 | 1919-06-12 | Seward Seymoure Vernon | Improvements in and relating to Compressed Air Power Plant. |
| JPS5930575U (en) * | 1982-08-23 | 1984-02-25 | いすゞ自動車株式会社 | Air compressor intake air blowback prevention device |
| EP0921309A1 (en) * | 1997-12-02 | 1999-06-09 | Poclain Hydraulics | Hydraulic motor with switch valve |
| JP2001303995A (en) * | 2000-04-26 | 2001-10-31 | Toyota Motor Corp | Internal combustion engine |
| US20110083434A1 (en) * | 2007-03-07 | 2011-04-14 | Thermal Power Recovery Llc | Method and Apparatus For Achieving Higher Thermal Efficiency In A Steam Engine or Steam Expander |
| CN102209836A (en) * | 2008-11-10 | 2011-10-05 | 河锡奉 | Cylinder driving apparatus using air pressure |
| CN102725532A (en) * | 2010-01-29 | 2012-10-10 | Ulvac机工株式会社 | Pump |
| CN102787866A (en) * | 2012-08-17 | 2012-11-21 | 彭学军 | Turbine engine using compressed air as working energy |
| CN106460514A (en) * | 2014-04-04 | 2017-02-22 | Z机械技术研究所有限公司 | Expander and air-freezing apparatus equipped with same |
| CN104454014A (en) * | 2014-10-21 | 2015-03-25 | 大连理工大学 | Compressed air engine-air compressor integrated dual-purpose machine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112648168B (en) | 2022-03-08 |
| JP6812532B1 (en) | 2021-01-13 |
| JP2021099089A (en) | 2021-07-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101321956B (en) | Fluid compressor with aerostatic bearing, control system of a compressor with aerostatic bearing and method of controlling a compressor with aerostatic bearing | |
| CN112648168B (en) | Reciprocating compression expander | |
| CN101545441B (en) | Gas starting device of engine | |
| CN203248303U (en) | Air starting system of diesel generator | |
| KR101253086B1 (en) | Energy saving device for oil injection type screw compressor | |
| CN112610442B (en) | Reciprocating compression expander | |
| US20110020148A1 (en) | Multi-stage rotary compressor | |
| US5860801A (en) | Rotary screw compressor with unloading means | |
| EP1798416B1 (en) | Rotary compressor with improved working efficiency and relative method | |
| CN101460705B (en) | Compressor device and method for remaking compressor or redesigning compressing device | |
| CN211924433U (en) | Oilless middle-high pressure air compressor | |
| JP2004339994A (en) | Screw compressor with balance piston device | |
| CN113785112A (en) | Compressed air storage power generation device | |
| WO2021002146A1 (en) | Compressed air storage electricity generating device | |
| WO2021039467A1 (en) | Compressed air storage electricity generating device | |
| US11255350B2 (en) | Method and apparatus for conversion of single-acting pneumatic actuator to electric power platform | |
| CN213144708U (en) | Gas compressor | |
| US11732733B2 (en) | Method and apparatus for conversion of a pneumatic actuator to an electric power platform | |
| KR100677515B1 (en) | Modulation type multi-stage rotary compressor and airconditioner using this | |
| JP5386532B2 (en) | Compressor | |
| CN201162608Y (en) | Gas starting device of engine | |
| US20240141882A1 (en) | Power system | |
| CN201539397U (en) | Air intake control valve | |
| JP2023047677A (en) | Compressor-cum-expander | |
| CN108981233A (en) | Variable-capacity compression assembly and variable-capacity air conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20230718 Address after: Tokyo Patentee after: Mitsui Yiaisi Co.,Ltd. Address before: Tokyo Patentee before: MITSUI ENGINEERING & SHIPBUILDING Co.,Ltd. |
|
| TR01 | Transfer of patent right |