KR20240038866A - A Diaphram Hydrogen Compressor Driving in Constant Temperature - Google Patents

Abstract

The present invention relates to a diaphragm hydrogen compressor driven at a constant temperature, the configuration of which includes a cylinder portion having a sliding piston therein, an oil flange portion extending to the tip of the cylinder portion, and a tip of the oil flange portion, A cover part provided on the upper surface with a valve for allowing gas to enter and exit the inside, a diaphragm dividing the space between the oil flange part and the cover part, and a plate-shaped space provided at the bottom of the cover part and recessed in the lower surface. Oil is supplied through a cavity plate provided, an oil plate formed in a plate shape with several through holes formed at the top of the oil flange section and a recessed space provided on the upper surface, and a flow path formed on the inner wall of the cylinder section. It is characterized by comprising a temperature control unit that maintains the cylinder unit at a constant temperature, and a crank unit provided at the other end of the piston to transmit power to move the piston.

Description

A Diaphram Hydrogen Compressor Driving in Constant Temperature}

The present invention relates to a diaphragm hydrogen compressor, and more specifically, to a diaphragm hydrogen compressor that operates at a constant temperature that can maintain a constant temperature from the initial operation.

Hydrogen energy is an alternative energy that can reduce national dependence on external energy resources, secure energy security and energy economy, and dramatically reduce greenhouse gases such as air pollution (SOx and NOx) due to the enforcement of the Kyoto Protocol. Hydrogen energy will be used nationally in the future. As part of the ongoing hydrogen energy infrastructure system construction, we are developing a high-pressure hydrogen compressor, which is a key device for supplying hydrogen to fuel cells, an energy generating device for automobiles, and hydrogen stations for automobile charging, to significantly reduce atmospheric environmental problems caused by transportation energy. It is a technology with enormous potential that can actively contribute to revitalizing the hydrogen economy.

Using this, looking at the contents described in Korean Patent Publication No. 10-0027848, in the hydrogen station that stores and supplies hydrogen for fuel cells, a hydrogen gas storage tank and compressor for storing the supplied hydrogen, a high-pressure hydrogen storage container, and ranking. At least two or more compressors including a control panel and a charger compressor for directly charging compressed hydrogen to the vehicle, compressing the hydrogen supplied from the hydrogen gas storage tank to a pressure suitable for a device using a fuel cell, and each of the compressors In the process of distributing compressed hydrogen gas connected in series to a high-pressure storage vessel mounted on a device using a fuel cell, at least two priority control panels that appropriately adjust the operation order using distribution valves at each stage of the high-pressure storage vessel; Several compressed hydrogen gas storage containers in which excess hydrogen gas compressed in the compressor is temporarily stored and supplied back to the priority control panel, and a fuel cell is used through a charging nozzle for hydrogen gas supplied through the priority control panel. It is composed of one or more hydrogen gas chargers that fill a high-pressure storage container mounted on the device and have functions such as pressure adjustment, metering, and billing of hydrogen gas, and are used to supply compressed hydrogen to facilities that use fuel cells, especially automobiles. It describes a hydrogen station that can be installed in the same form as a gas station.

In particular, in the case of compressors, diaphragm compressors are mainly used among various compressors. As shown in FIG. 1, in the diaphragm compressor, a diaphragm separates a lower hydraulic fluid chamber and an upper fluid chamber. The hydraulic fluid chamber is a part of the hydraulic fluid system that moves a piston to build pressure within the hydraulic fluid chamber.

The pressure causes the diaphragm to move toward the fluid chamber, pressurizing the fluid in the hydraulic fluid chamber. Hydraulic fluid is injected with each cycle to ensure full displacement of the diaphragm and to compensate for leakage, for example in the piston. When the diaphragm reaches full displacement and the piston still has not completed its discharge stroke, excess hydraulic fluid within the hydraulic fluid chamber exits the hydraulic fluid chamber through a passage leading to a hydraulic fluid reservoir in the hydraulic fluid system.

However, the prior art had the following problems.

When the piston of the compressor cylinder is initially driven, the temperature of the cylinder and coolant is low, so there is a problem in which the performance of the compressor deteriorates until the temperature rises to a certain level.

Public Patent No. 10-2020-0037802

In order to solve the above-described problems, the purpose of the present invention is to provide a diaphragm hydrogen compressor that operates at a constant temperature that can maintain a constant temperature from the initial operation.

In order to achieve the above-described object, the present invention's diaphragm hydrogen compressor driven at constant temperature includes a cylinder portion provided with a sliding piston therein, an oil flange portion extending to the tip of the cylinder portion, and a tip of the oil flange portion. It is provided in the cover part, the upper surface of which is provided with a valve through which gas enters and exits the inside, a diaphragm that divides the space between the oil flange part and the cover part, and a plate-shaped diaphragm, which is provided at the bottom of the cover part, and is provided on the lower surface. A cavity plate provided with a recessed space, an oil plate formed in a plate shape with several through holes formed at the top of the oil flange section and provided with a recessed space on the upper surface, and a flow path formed on the inner wall of the cylinder section. It is characterized by comprising a temperature control unit that supplies oil to maintain the cylinder unit at a constant temperature, and a crank unit provided at the other end of the piston to transmit power to move the piston.

It is characterized in that the space of the oil plate is made larger than the space of the cavity plate.

The space of the cavity plate is divided into a first space and the space of the oil plate part is divided into a second space, and when the total volume of the space is 10, the first space has a volume ratio of 0 and the second space is It is characterized by being formed at a volume ratio of 10.

The diaphragm hydrogen compressor operated at constant temperature according to the present invention has the following effects.

By allowing the oil heater to selectively flow inside the cylinder case from the initial operation of the cylinder, the temperature of the cylinder is always maintained at a constant level, which has the advantage of increasing overall compressor efficiency.

1 is a schematic diagram showing the structure of a diaphragm hydrogen compressor.
Figure 2 is a diagram showing the schematic configuration of a diaphragm hydrogen compressor according to the prior art.
Figure 3 is a diagram showing the schematic configuration of a diaphragm hydrogen compressor according to the present invention.
Figure 4 is a diagram showing the operation process of the diaphragm hydrogen compressor according to the present invention.
Figure 5 is a cross-sectional view showing the structure of the cylinder, oil flange, and oil plate of the diaphragm hydrogen compressor employing another embodiment of the oil plate in the diaphragm hydrogen compressor according to the present invention.
Figure 6 is a cross-sectional view showing the section of Figure 5.
Figure 7 is a diagram showing the stress generated when 100 MPa pressure is applied to the surface of the diaphragm of the diaphragm hydrogen compressor according to the present invention.
Figure 8 is a graph showing the stress reduction rate generated when 100 MPa pressure is applied to the surface of the diaphragm of the diaphragm hydrogen compressor according to the present invention.

Hereinafter, a preferred embodiment of a diaphragm hydrogen compressor operating at constant temperature according to the present invention will be described in detail with reference to the attached drawings.

As shown in FIG. 1, the diaphragm hydrogen compressor of the present invention, which operates at a constant temperature, includes a cylinder part 10 provided with a sliding piston 12 therein, and an oil plane extending to the tip of the cylinder part 10. A branch 20, a cover part 30 provided at the tip of the oil flange part 20 and a valve 32 on the upper surface through which gas flows in and out, the oil flange part 20 and the A diaphragm 40 that partitions the space of the cover part 30, a cavity plate 50 formed in a plate shape and provided at the bottom of the cover part 30 and providing a recessed space in the lower surface, and a plate shape. An oil plate 60 having several through holes 62 formed at the top of the oil flange portion 20 and providing a recessed space on the upper surface, and an oil plate 60 provided at the other end of the piston 12 to form the piston 12. It includes a crank unit 70 that transmits power to move the cylinder unit 10, and a temperature control unit 80 that supplies oil to a channel formed on the inner wall of the cylinder unit 10 to maintain the cylinder unit 10 at a constant temperature. And, the space of the oil plate 60 can be made larger than the space of the cavity plate 50.

First, the diaphragm hydrogen compressor of the present invention is provided with a cylinder unit 10. The cylinder part 10 has a space inside, and a piston 12 that can slide along the space is provided in the space.

An oil flange portion 20 is provided at the tip of the cylinder portion 10. The oil flange portion 20 has a recessed space on its upper surface where the oil plate 60, which will be described below, is located, and is configured to communicate with the tip of the cylinder portion 10 to allow fluid to flow.

A cover portion 30 is provided at the tip of the oil flange portion 20. The cover part 30 has a recessed space on the lower surface where the cavity plate 50, which will be described below, is located, and the cover part 30 allows external gas to enter and exit the cover part 30. A valve 32 is provided.

The valve 32 communicates with the cover part 30 and the cavity plate 50 and guides gas into and out of the internal space of the cavity plate 50.

A diaphragm 40 is provided between the oil flange portion 20 and the cover portion 30. The diaphragm 40 serves to partition the space formed by the oil flange portion 20 and the cover portion 30. More specifically, it serves to partition the space formed by the cavity plate 50 and the oil plate 60, which will be explained below.

The diaphragm 40 serves to transmit power to compress the flow of fluid generated by the operation of the piston 12 of the cylinder 10 by moving gas flowing in and out through the valve 32.

Also, a cavity plate 50 is provided on the lower surface of the cover part 30. The cavity plate 50 is formed in a plate shape and communicates with the cover portion 30 and the valve 32 to guide external gas to enter and exit the lower side of the cavity plate 50.

A recessed first space 51 is provided below the cavity plate 50. The first space 51 is a space through which external gas can enter and exit through the valve 32, and the gas flowing into the first space 51 is compressed by the up and down movement of the diaphragm 40. .

An oil plate 60 is provided on the upper surface of the oil flange portion 20. The oil plate 60 is formed in a plate shape and serves to prevent the piston 12 from directly affecting the diaphragm 40.

A recessed second space 61 is provided on the upper surface of the oil plate 60. The second space 61 serves to guide the downward movement range of the diaphragm 40. That is, when the diaphragm 40 moves to the bottom dead center in the suction stroke, the range in which the diaphragm 40 moves downward is limited.

The first space 51 and the second space 61 may be configured differently. The first space 51 may be formed to be relatively small in size compared to the second space 61 . This means that during the compression stroke caused by the operation of the piston 12 of the cylinder 10, the diaphragm 40 receives a lot of pressure when it contacts the top dead center, that is, the inner wall of the first space 51. This is to reduce the influence on pressure by limiting the movement range of the diaphragm (40) by reducing (51).

The ratio of the first space 51 and the second space 61 is set to 0 when the total volume of the space is 10, and the diaphragm 40 is set at the top dead center of the piston 12. ) It is desirable that there is no deformation of .

When the first space 51 is formed, strong pressure and deformation occur simultaneously in the diaphragm 40, resulting in the diaphragm 40 being easily damaged. Even if there is no first space 51 at all, the first space 51 is formed as the diaphragm 40 moves downward and compression occurs.

Several through holes 62 are formed in the oil plate 60. Through the hole 62, the fluid moving by the movement of the piston 21 transmits power to the diaphragm 40 to operate.

A guide groove 63 is provided in the oil plate 60. The guide groove 63 is formed on the lower surface of the oil plate 60 and is formed at a portion where the tip of the piston 12 touches. The guide groove 63 serves to prevent the through hole 62 from blocking the flow of fluid when the tip of the piston 12 touches the lower surface of the oil plate 60.

The guide groove 63 may be configured as shown in FIGS. 5 and 6. The guide groove 63 is formed radially around the center of the lower surface of the oil plate 60, and through holes 62 may be formed in the guide groove 63.

In addition, the guide groove 63 specifically includes a first guide groove 64 recessed in a circular shape at the center of the oil plate 60, and a second guide groove 64 recessed in a ring shape at the edge of the oil plate 60. It includes a guide groove (66) and a third guide groove (65) radially connecting the first guide groove (64) and the second guide groove (66), and the first guide groove (64) The through holes 62 may be formed in the second guide groove 66 and the third guide groove 65.

As the oil compressed by the piston 12 moves without resistance along the first guide groove 64, the second guide groove 65, and the third guide groove 66, a hole 62 is formed in each of the first guide groove 64, the second guide groove 65, and the third guide groove 66. It moves through.

And, a crank portion 70 is provided at the other end of the piston 12. The crank unit 70 serves to provide power so that the piston 12 slides.

A temperature control unit 80 is provided in the cylinder unit 10. The temperature control unit 80 controls the temperature of the inner wall of the cylinder unit 10 so that the cylinder unit 10 can always maintain a constant temperature.

That is, the temperature control unit 80 serves to increase the temperature of the cylinder unit 10 by preheating it before driving.

The temperature control unit 80 may be configured in various ways for the above-described functions, and may be configured as follows.

The temperature control unit 80 includes a connection passage 82 that communicates with the passage flowing through the internal heat exchanger 81 on the wall of the cylinder unit 10, and a pump that supplies oil through the connection passage 82 ( 84) and a heat exchanger 86 that heats the temperature of the oil moving from the pump 84 to the connection passage 82.

In the temperature control unit 80, the medium moves along the connection passage 82, and when the cylinder unit 10 is at a low temperature, the medium is heated through the heat exchange unit 86 to heat the cylinder unit 10. is transmitted to the flow path to increase the temperature of the cylinder unit 10.

In addition, the diaphragm compressor of the present invention may be separately provided with a cooling unit (not shown) to prevent the cylinder unit 10 from overheating, and the temperature may be kept constant by cooling through the temperature control unit 80.

Next, the stress generated in the diaphragm when the first space 51 and the second space 61 were changed in the diaphragm compressor of the present invention was analyzed. When a pressure of 100 MPa is applied to the diaphragm surface, the stress generated in the diaphragm is shown by changing the ratio of the first space, which is the space ratio of the cavity plate, from 50% to 0%.

[Comparative example]

The size of the first space of the cavity plate and the second space of the oil plate were made the same, that is, the first space was formed with a volume ratio of 50%, and then the crank unit was driven to compress the gas flowing into the first space to 100 MPa. .

[Example 1]

When the total size of the first space and the second space is 100, the size of the first space of the cavity plate is set to a volume ratio of 0%, the size of the second space of the oil plate is set to a volume ratio of 100%, and then the crank By driving the unit, the gas flowing into the first space was compressed to 100 MPa.

[Example 2]

When the total size of the first space and the second space is 100, the size of the first space of the cavity plate is formed with a volume ratio of 10.8%, the size of the second space of the oil plate is formed with a volume ratio of 89.2%, and then the crank By driving the unit, the gas flowing into the first space was compressed to 100 MPa.

[Example 3]

When the total size of the first space and the second space is 100, the size of the first space of the cavity plate is formed with a volume ratio of 21.7% and the size of the second space of the oil plate is formed with a volume ratio of 78.3%, and then cranked. By driving the unit, the gas flowing into the first space was compressed to 100 MPa.

[Example 4]

When the total size of the first space and the second space is 100, the size of the first space of the cavity plate is formed with a volume ratio of 32.6%, and the size of the second space of the oil plate is formed with a volume ratio of 67.4%, and then cranked. By driving the unit, the gas flowing into the first space was compressed to 100 MPa.

[Example 5]

When the total size of the first space and the second space is 100, the size of the first space of the cavity plate is formed at a volume ratio of 43.5%, and the size of the second space of the oil plate is formed at a volume ratio of 56.5%, and then cranked. By driving the unit, the gas flowing into the first space was compressed to 100 MPa.

Comparative example Example 1 Example 2 Example 3 Example 4 Example 5 Maximum stress ratio according to first space ratio 100% 20% 38% 54% 72% 91%

As shown in Table 1 and Figures 7 and 8, when a pressure of 100 MPa is applied to the diaphragm surface, the stress generated in the diaphragm is reduced by changing the ratio of the first space of the cavity plate to 50% to 0%. When the space ratio of the first space is 50% with respect to 0% of the first space, the stress decreases by 80%, and when the first space ratio is 30%, the stress decreases by 30% with respect to the first space ratio of 50%. It will deteriorate.

That is, from the results of Examples 1 to 5, it was confirmed that by reducing the ratio of the first space to 100 MPa, the stress generated in the diaphragm could be reduced and the contribution of fatigue failure elements could be reduced.

As such, a person skilled in the art will understand that the technical configuration of the present invention described above can be implemented in other specific forms without changing the technical idea or essential features of the present invention.

Therefore, the embodiments described above should be understood in all respects as illustrative and not restrictive, and the scope of the present invention is indicated by the claims described later rather than the detailed description above, and the meaning and scope of the claims and their All changes or modified forms derived from the equivalent concept should be construed as falling within the scope of the present invention.

10: cylinder part 12: piston
20: Oil flange part 30: Cover part
32: valve 40: diaphragm
50: cavity plate 51: first space
60: Oil plate 61: Second space
62: Tonggong 63: Information home
64: 1st guide groove 65: 3rd guide groove
66: Second guide groove 70: Crank section
80: Temperature control unit

Claims (3)

A cylinder portion provided with a sliding piston therein;
An oil flange portion extending from the tip of the cylinder portion;
A cover portion provided at the tip of the oil flange portion and having a valve on the upper surface through which gas enters and exits the inside;
A diaphragm defining a space between the oil flange portion and the cover portion;
A cavity plate formed in a plate shape and provided at the bottom of the cover part to provide a recessed space on the lower surface;
An oil plate formed in a plate shape with several through holes provided at the top of the oil flange portion and having a recessed space on the upper surface;
a temperature control unit that supplies oil to a channel formed on the inner wall of the cylinder unit to maintain the cylinder unit at a constant temperature; and
A diaphragm hydrogen compressor driven at a constant temperature, comprising a crank provided at the other end of the piston and transmitting power to move the piston. According to clause 1,
A diaphragm hydrogen compressor driven at constant temperature, characterized in that the space of the oil plate is made larger than the space of the cavity plate. According to clause 1,
The space of the cavity plate is divided into a first space and the space of the oil plate part is divided into a second space, and when the total volume of the space is 10, the first space has a volume ratio of 0 and the second space is A diaphragm compressor driven at constant temperature, characterized in that it is formed with a volume ratio of 10.