JPWO2006003871A1 - Booster pump and cryogenic fluid storage tank equipped with the same - Google Patents

Abstract

Provided are a booster pump capable of efficiently boosting a fluid without heating the fluid, and a cryogenic fluid storage tank including the same. A booster pump comprising: a piston having a piston head and a piston rod; and a cylinder that houses the piston head and has a pressurizing chamber in which fluid is compressed by one end face of the piston head, A bellows for separating the space on the piston rod side and the space on the cylinder side of the pressurizing chamber is provided.

Description

  The present invention relates to a booster pump that compresses and pressurizes a low-temperature fluid, and a low-temperature fluid storage tank including the same.

Conventionally, as a booster pump for compressing and pressurizing a low-temperature (for example, about −273 ° C. to −0 ° C. or less) fluid (for example, hydrogen, nitrogen, LNG, etc.) What has it is known (for example, refer nonpatent literature 1).
Endo Takuya et al., “New Energy Vehicle”, Sankai-do, January 1995, p. 221-222

However, in such a conventional booster pump (for low-temperature fluid), the piston ring slides while the outer peripheral surface of the piston ring is pressed against the inner peripheral surface of the cylinder in order to maintain airtightness. There is a problem that heat is generated by friction between the cylinder and the cylinder, and the fluid is heated by the heat. In particular, when trying to obtain a high pressure, the high-pressure fluid that flows into the inner peripheral surface of the piston ring acts so that the outer peripheral surface of the piston ring is pressed more strongly against the inner peripheral surface of the cylinder. There was a problem that the friction between the piston ring and the cylinder became intense, and the heat generated by the friction significantly increased.
In addition, a slight gap is inevitably formed between the outer peripheral surface of the piston ring and the inner peripheral surface of the cylinder, and fluid leaks (leaks) from this gap, resulting in a reduction in compression efficiency. There was a problem.
Further, in such a conventional booster pump (for low temperature fluid), when compressing the low temperature fluid, the piston rod located between the piston head and the drive device is prevented from buckling due to the compression force. Therefore, there is a problem that heat from the driving device is transmitted to the low temperature fluid via the piston rod and the piston head, and the low temperature fluid is heated and boiled off.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a booster pump capable of efficiently increasing the pressure without heating the fluid, and a cryogenic fluid storage tank including the same.

In order to solve the above problems, the present invention employs the following means.
The present invention is a booster pump comprising: a piston having a piston head and a piston rod; and a cylinder that houses the piston head and has a pressurizing chamber in which fluid is compressed by one end surface of the piston head, The piston head is provided with a booster pump provided with a bellows for separating a space on the piston rod side and a space on the cylinder side of the pressurizing chamber.
According to the present invention, the space on the piston rod side of the pressurizing chamber and the space on the cylinder side are separated by the bellows, and the portion that moves in contact with the inner peripheral surface of the pressurizing chamber (for example, the conventional Therefore, the heat generation in the pressurizing chamber is prevented and the fluid is prevented from being heated.
In addition, since the space on the piston rod side of the pressurizing chamber and the space on the cylinder side are completely separated by the bellows, the fluid from the cylinder side of the pressurizing chamber to the piston rod side of the pressurizing chamber Leakage (leakage) is prevented, and pump efficiency is improved.

In the said invention, it is preferable that the filler which fills the space which exists between the outer surface of the said bellows and the internal peripheral surface of the said cylinder is arrange | positioned.
As a result, the gap between the outer surface of the bellows and the inner peripheral surface of the pressurizing chamber is filled, the dead volume of the pressurizing chamber is reduced, and the pump efficiency is improved.

In the said invention, it is preferable that the ring-shaped sealing member is arrange | positioned at the one end part by the side of the piston head of the said bellows.
As a result, the leakage of fluid from the one end surface side of the piston head to the other end surface side is reduced by the seal member, and the pressure applied to the outer peripheral surface of the bellows is reduced. A low-pressure bellows can be used, the piston stroke can be increased, and the compression efficiency (pump efficiency) can be increased.
This seal member does not have the tension as the piston ring, which has been regarded as a problem in the past, and the stroke of the piston is greatly restricted by the bellows (the stroke is small). Never generate heat.

In the said invention, it is preferable that the said piston rod is made into the heat insulation vacuum structure hollow and evacuated.
The piston rod has a hollow structure, which reduces the weight of the piston rod and allows the piston to be pushed up with a low load. Heat entry from the rod into the fluid can be reduced.

The present invention provides at least two booster pumps, and a booster pump that performs multi-stage compression by these booster pumps.
According to the present invention, for example, in the case where two boosting pumps are provided, one low pressure pump and the other high pressure pump are used so that the low pressure pump has a low pressure bellows. Because it can be used, the piston stroke can be increased, and the fluid can be easily boosted from low pressure to intermediate pressure. In addition, the high pressure pump can use a high pressure bellows, so the piston stroke can be increased. Although it cannot be taken, the fluid can be easily raised from an intermediate pressure to a high pressure.
That is, if the pressure of the fluid is to be increased from low pressure to high pressure by using only one booster pump, the high pressure bellows must be used as the bellows, and the stroke cannot be made large. It was difficult to increase the pressure to (high pressure).
On the other hand, as described above, the fluid can be easily boosted to a desired pressure by compressing the fluid in two stages using, for example, two pumps.

The present invention is a cryogenic fluid storage tank for storing cryogenic fluid at a low temperature, the boosting pump or the boosting device, the cryogenic fluid storage tank in which the cryogenic fluid is stored, the boosting pump or the boosting device. And a cryogenic fluid storage tank comprising a cryogenic container in which the cryogenic fluid storage tank is accommodated.
According to the present invention, since the booster pump or the booster device is arranged in the low temperature container, the booster pump or the booster device is forcibly cooled and it is difficult to raise the temperature.

In the said invention, it is preferable that the said pressure | voltage rise pump or the said pressure | voltage rise apparatus is arrange | positioned in the downstream of the said low temperature fluid storage tank, and the outer side of the said low temperature fluid storage tank.
Since the booster pump or the booster device is disposed outside the cryogenic fluid storage tank (that is, provided separately from the cryogenic fluid storage tank in the adiabatic vacuum tank of the cryogenic container), The heat generated by the drive source is prevented from being transferred to the cryogenic fluid stored in the cryogenic fluid storage tank, and the temperature rise and evaporation of the cryogenic fluid is prevented.

In the said invention, it is preferable that the low-temperature slush-like fluid which is a solid-liquid two-phase state is stored in the said low-temperature fluid storage tank.
A slush-like cryogenic fluid (solid cryogenic fluid and liquid cryogenic fluid mixed in a sherbet form) is stored in the cryogenic fluid storage layer, so that only liquid cryogenic fluid is stored. However, it is difficult to evaporate, the suction performance of the booster pump or the booster device is improved, and the supply amount of the low-temperature fluid is increased.

In the said invention, it is preferable that the mesh is arrange | positioned at the exit of the said cryogenic fluid storage tank.
The solid cryogenic fluid of the slush fluid is captured by the mesh, and only the liquid cryogenic fluid is supplied to the booster pump or the booster device located downstream of the cryogenic fluid storage tank, The clogging of the booster pump or the booster is prevented.

In the said invention, it is preferable that the heater is arrange | positioned in the said cryogenic fluid storage tank.
As a result, the solid cryogenic fluid in the cryogenic fluid storage tank is heated by the heater to be changed into a liquid cryogenic fluid, and then supplied to the booster pump or the booster through the mesh. .

In the said invention, it is preferable that the heat exchanger is arrange | positioned in the downstream of the said pressure | voltage rise pump or the pressure | voltage rise apparatus.
As a result, the low-temperature fluid that has passed through the booster pump or booster by the heat exchanger is vaporized (gasified) by the heat exchanger, and then supplied to the engine etc. located on the downstream side and consumed immediately by the engine etc. It has become so.

In the said invention, it is preferable that the radiation shield board is provided in the inner surface of the said cryogenic container.
As a result, the radiation shield plate prevents heat from entering from the outside to the inside of the cryogenic container, and prevents the heat insulating vacuum layer in the cryogenic container from rising in temperature.

The present invention includes a cylinder block having a pressurizing chamber therein, a piston head that is housed in the pressurizing chamber and reciprocates in the pressurizing chamber, and a low-temperature fluid is caused by one end surface of the piston head. A pressurizing pump for a low-temperature fluid to be compressed, wherein an inner peripheral space and an outer periphery of the piston head are disposed between one end surface of the piston head and an inner surface of the pressurizing chamber facing the one end surface. Provided is a cryogenic fluid booster pump provided with a flexible partition member that separates a side space.
According to the present invention, when the piston head moves in one direction, the internal space of the partition member (that is, the space formed by one end surface of the piston head, the inner peripheral surface of the partition member, and the inner surface of the pressurizing chamber). The low-temperature fluid is sucked (supplied) into the inside, and the piston head moves in the other direction, whereby the low-temperature fluid is compressed (pressurized) to a predetermined pressure.
That is, between the piston head and the inner peripheral surface of the pressurizing chamber, and between the partition member and the inner peripheral surface of the pressurizing chamber, a portion that moves while in contact with each other (such as a conventional piston ring) ), It is possible to prevent heat generation in the pressurizing chamber and to prevent the low-temperature fluid from being heated.
Further, since the inner circumferential side (radially inner side) and the outer circumferential side (radial outer side) of the pressurizing chamber are completely separated by the partition member, the outer periphery of the pressurizing chamber is separated from the inner peripheral side of the pressurizing chamber. The leakage of the low temperature fluid from the outer side (or the outer peripheral side of the pressurizing chamber to the inner peripheral side of the pressurizing chamber) can be prevented, and the compression efficiency of the booster pump for the low temperature fluid can be improved.

In the said invention, it is preferable that the pressurized fluid is filled into the outer side of the said partition member.
The outside of the partition member is filled (supplied) with, for example, a gasified low-temperature fluid having a predetermined pressure, and the pressure difference between the inside and the outside of the partition member is reduced (approached).
That is, outside the partition member (outside in the radial direction), for example, it is heated and gasified by a heat exchanger, and the pressure is regulated by a pressure regulator to a predetermined pressure (for example, half of the boosting force of the booster pump) Therefore, the deformation of the partition member when compressing the low-temperature fluid sucked into the internal space of the partition member can be reduced. The service life can be extended, and the reliability of the booster pump for low-temperature fluid can be improved.

In the said invention, it is preferable that the outer side of the said partition member is made into the vacuum state.
That is, the space between the partition member and the cylinder block is in a vacuum state, and heat inside the partition member (that is, heat of the low-temperature fluid compressed inside the partition member) is transmitted to the cylinder block. To prevent that.
Thereby, while the temperature rise of a cylinder block is suppressed, the temperature rise of the low-temperature fluid which flows in into a pressurization chamber will be suppressed.

The present invention includes a piston rod driven by a drive unit connected to a drive source, a piston head connected to the piston rod and reciprocating with the piston rod, the piston head being housed, And a cylinder having a pressurizing chamber in which a cryogenic fluid is compressed by one end face, wherein the driving unit is disposed on the one end face side of the piston head and compresses the cryogenic fluid. A booster pump for low-temperature fluid is provided in which a pulling force in a direction substantially the same as the extending direction of the shaft portion is applied to the shaft portion of the piston rod.
According to the present invention, when the piston rod is pulled toward the drive unit, the low-temperature fluid is compressed by the one end surface of the piston head. That is, the compression force is not applied to the piston rod when compressing the low-temperature fluid.
As a result, the diameter of the piston rod can be made smaller than that of a conventional piston rod in which a compression force is applied to the piston rod, so that heat input from the drive source can be reduced and the weight of the piston rod can be reduced. And the weight of the entire pump can be reduced.
Moreover, when compressing a low temperature fluid, it is comprised so that a compression force may not be applied to a piston rod, Therefore The diameter of a piston head can be enlarged. That is, in the conventional pump in which the compression force is applied to the piston rod, the diameter of the piston head is limited to, for example, a diameter of 40 mm in order to avoid buckling of the piston rod. Therefore, in the conventional pump, for example, five cylinders are required to secure the flow rate of the low-temperature fluid. However, in the pump of the present invention, the diameter of the piston head can be set to, for example, 100 mm. Even with a single cylinder, a sufficient flow rate can be secured.
Thereby, in the pump by this invention, while being able to simplify the structure of a pump, the weight reduction and diameter reduction of the whole pump can be achieved.

In the above invention, the piston head is divided into at least two members having concentric circles, and the cryogenic fluid is gradually brought to a desired pressure by sequentially passing through one end surfaces of the divided piston heads. It is preferable to have a multistage compression structure in which the pressure is increased to a maximum.
The piston head is divided into, for example, a radially outer member and a radially inner member, and the first compression (first stage compression) is performed by the radially outer member, and the radially inner member is Instead of trying to pressurize the low-temperature fluid from low pressure to high pressure at once, by performing the second compression (second-stage compression), pressurize the low-temperature fluid once to the intermediate pressure, The pressure (high pressure) is increased.
Thereby, since the stroke of the piston head can be reduced, the length of the entire pump in the vertical direction can be shortened, and the pump can be downsized.

In the above invention, a flexible partition member for separating the piston rod side space and the cylinder side space of the pressurizing chamber is provided on one end surface side and the other end surface side of the piston head, respectively. Preferably it is.
The space on the piston rod side of the pressurizing chamber and the space on the cylinder side are separated by a partition member, and the part that moves in contact with the inner peripheral surface of the pressurizing chamber (for example, a conventional piston ring Therefore, the heat generation in the pressurizing chamber is prevented and the low temperature fluid is prevented from being heated.
Further, the space on the piston rod side of the pressurizing chamber and the space on the cylinder side are completely separated by the partition member, so that the cylinder side of the pressurizing chamber is moved to the piston rod side of the pressurizing chamber. Leakage of the low-temperature fluid is prevented, and the compression efficiency is improved.

In the said invention, it is preferable that the partition member which has the flexibility which isolate | separates the space on the piston rod side of the said pressurization chamber, and the space on the cylinder side is provided in the other end surface side of the said piston head.
As a result, all of the flexible partition members are provided on the side opposite to the one end surface (compression surface) of the piston head, so that the length in the height direction (longitudinal direction) of the pump is shortened. The pump can be downsized.
In addition, since the area of one end surface (compression surface) of the piston head can be utilized to the maximum for compression of low-temperature fluid, more low-temperature fluid can be compressed at a time, resulting in higher pump efficiency (high capacity) ).

In the said invention, it is preferable that the pre-cooling layer is formed in the said cylinder.
As a result, the entire pump can be sufficiently cooled in advance before starting the pump, so that gasification (boil-off) of the low-temperature fluid supplied to the pump can be reduced.
In addition, since the pre-cooling layer serves as a heat insulating layer even during the pump operation, gasification (boil-off) of the low-temperature fluid can be reduced even during the pump operation.

In the said invention, it is preferable that the said drive part and the said piston rod are connected via the heat insulation connection part.
Since the drive unit and the piston rod are connected to each other by, for example, point contact or line contact via a rolling element (for example, a ball or a roller), the piston rod is connected to the drive unit (ie, the drive source). In other words, the transfer of heat (heat input) to the piston head is greatly interrupted.

In the said invention, it is preferable that the said piston head and the said piston rod are connected via the heat insulating material.
Since the piston head and the piston rod are connected via a heat insulating material, even if there is heat transfer (heat input) from the drive unit to the piston rod, the piston rod to the piston head This heat transfer (heat input) is blocked by the heat insulating material.

In the said invention, it is preferable that the guide member which guides the axial part of the said piston rod is provided between the said cylinder and the said piston rod.
A guide member is provided so that a piston rod, a piston head, and the like that are housed in the cylinder and reciprocate in the cylinder do not collide with the inner wall surface (cylinder wall) of the cylinder.
As a result, the reciprocating members such as the piston rod and the piston head reciprocate without shaking or vibrating in the cylinder, and the reciprocating member can be prevented from colliding with the inner wall surface of the cylinder. In addition, the reciprocating member can be smoothly driven with minimal power.

In the said invention, it is preferable that the space between the said cylinder and the axial part of the said piston rod is comprised so that it may be in a vacuum state.
That is, the space between the cylinder and the piston rod is in a vacuum state, and heat from the piston rod (that is, heat that has entered the piston rod side from the drive source side) is prevented from being transmitted to the cylinder. is doing.
Thereby, while the temperature rise of a cylinder is suppressed, the temperature rise of the low temperature fluid which flows in into a pressurization room will be controlled.

In the said invention, it is preferable that the said cylinder is comprised so that attachment or detachment with respect to the said cryogenic fluid storage tank is carried out while being immersed in the cryogenic fluid stored inside the cryogenic fluid storage tank.
As a result, the outside of the portion that accommodates the portion that compresses the low-temperature fluid, such as the cylinder and the piston head, is immersed in the low-temperature fluid, and is always maintained at a low temperature. In addition, the cylinder is installed in a form that can be easily replaced at the lower part (bottom part) of the cryogenic fluid storage tank.

The drive unit and the cylinder are preferably configured to be immersed in a cryogenic fluid stored in a cryogenic fluid storage tank and to be detachable from the cryogenic fluid storage tank.
As a result, the outside of the entire pump including the part that accommodates the part that compresses the low-temperature fluid, such as the cylinder and the piston head, is immersed in the low-temperature fluid and always kept at a low temperature. Moreover, the booster pump for low temperature fluid will be installed in the lower part (bottom part) of the storage tank for low temperature fluid with the form easy to replace.

The present invention includes a low-temperature fluid boost pump, a chamber for storing a low-temperature fluid boosted by the low-temperature fluid boost pump, and a fuel injection device supplied with the low-temperature fluid from the chamber. A fluid supply apparatus is provided.
According to the present invention, the cryogenic fluid boosted to a desired pressure by the cryogenic fluid booster pump is temporarily stored in a chamber located downstream of the cryogenic fluid booster pump, and then passes through the fuel injection device. For example, the fuel is injected into a combustion chamber such as an engine.

In the above-described invention, a pressurized fluid supply unit is provided in which the cryogenic fluid in the chamber is liquefied or gasified and supplied into the cylinder located on the other end face side of the piston head of the cryogenic fluid booster pump. Preferably it is.
As a result, the cryogenic fluid in the chamber (or the cryogenic fluid in the chamber is liquefied or gasified and decompressed by, for example, a pressure regulator) is supplied into the cylinder located on the other end surface side of the piston head. Thus, the difference between the pressure on the one end surface (compression surface) side of the piston head and the pressure on the other end surface side can be reduced, and a bellows having low pressure resistance can be used.

In the above invention, the low-temperature fluid in the chamber is gasified on the path to the fuel injection device, and is supplied into the cylinder located on the other end face side of the piston head of the high-pressure fluid boost pump. It is preferable that a supply unit is provided.
As a result, the low-temperature fluid in the chamber (or the low-temperature fluid in the chamber that has been decompressed with a pressure regulator or the like in a gasified state) is supplied into the cylinder located on the other end surface side of the piston head. The difference between the pressure on the one end surface (compression surface) side of the piston head and the pressure on the other end surface side can be reduced, and a bellows having low pressure resistance can be used.

In the said invention, it is preferable that the said chamber is provided with the relief valve.
As a result, when the pressure in the chamber in which the cryogenic fluid is accumulated exceeds a predetermined pressure, the relief valve is activated to prevent the chamber from being damaged. For example, the low-temperature fluid ejected from the relief valve is configured to be returned to the suction side of the pump (or a fuel cell provided with a separate fuel cell) via a return pipe.

The present invention includes a cylinder block having a pressurizing chamber therein, a piston head that is housed in the pressurizing chamber and reciprocates in the pressurizing chamber, and a low-temperature fluid is caused by one end surface of the piston head. A pressurizing pump for a low-temperature fluid to be compressed, provided on the other end surface side of the piston head with a flexible partition member that separates an inner peripheral space and an outer peripheral space of the pressurizing chamber A booster pump for a cryogenic fluid is provided.
According to the present invention, when the piston head moves in one direction, the cryogenic fluid is sucked (supplied) into the pressurizing chamber, and when the piston head moves in the other direction, the cryogenic fluid is compressed (pressurized) to a predetermined pressure. Will be.
That is, between the piston head and the inner peripheral surface of the pressurizing chamber, and between the partition member and the inner peripheral surface of the pressurizing chamber, a portion that moves while in contact with each other (such as a conventional piston ring) ), It is possible to prevent heat generation in the pressurizing chamber and to prevent the low-temperature fluid from being heated.
Further, since the inner circumferential side (radially inner side) and the outer circumferential side (radial outer side) of the pressurizing chamber are completely separated by the partition member, the outer periphery of the pressurizing chamber is separated from the inner peripheral side of the pressurizing chamber. The leakage of the low temperature fluid from the outer side (or the outer peripheral side of the pressurizing chamber to the inner peripheral side of the pressurizing chamber) can be prevented, and the compression efficiency of the booster pump for the low temperature fluid can be improved.

In the said invention, it is preferable that the pressurized fluid is filled inside the said partition member.
The inside of the partition member is filled (supplied) with, for example, a gasified low-temperature fluid having a predetermined pressure, and the pressure difference between the inside and the outside of the partition member is reduced (approached).
That is, on the inner side (radially inner side) of the partition member, for example, it is heated and gasified by a heat exchanger, and the pressure is adjusted to a predetermined pressure (for example, half of the boosting force of the booster pump by the pressure regulator). Therefore, it is possible to reduce deformation of the partition member when compressing the low-temperature fluid sucked into the pressurizing chamber, and to increase the service life of the partition member. Therefore, the reliability of the booster pump for low-temperature fluid can be improved.

In the said invention, it is preferable that the inner side of the said partition member is made into the vacuum state.
Thereby, for example, even when there is a piston rod or the like connected to the piston head inside the partition member, the heat from the piston rod (for example, heat that has entered the piston rod side from the drive source side) is the partition member. Is prevented from being transmitted outside.
Thereby, while the temperature rise of the cylinder block located in the outer side of a partition member is suppressed, the temperature rise of the low temperature fluid which flows in into a pressurization chamber will be suppressed.

In the said invention, it is preferable that the guide member which guides the said piston head is provided between the said cylinder block and the said piston head.
A guide member is provided so that a piston rod, a piston head, and the like that are housed in the cylinder and reciprocate in the cylinder do not collide with the inner wall surface (cylinder wall) of the cylinder.
As a result, the reciprocating members such as the piston rod and the piston head reciprocate without shaking or vibrating in the cylinder, and the reciprocating member can be prevented from colliding with the inner wall surface of the cylinder. In addition, the reciprocating member can be smoothly driven with minimal power.

In the said invention, it is preferable that the said cylinder block is comprised so that attachment or detachment with respect to the said cryogenic fluid storage tank is carried out while being immersed in the cryogenic fluid stored inside the cryogenic fluid storage tank.
As a result, the outside of the portion accommodating the portion that compresses the low-temperature fluid, such as the cylinder block and the piston head, is immersed in the low-temperature fluid and is always maintained at a low temperature. In addition, the cylinder block is installed in a form that can be easily replaced at the lower part (bottom part) of the cryogenic fluid storage tank.

  According to the present invention, there is an effect that the pressure can be increased efficiently without heating the fluid.

1 is a schematic longitudinal sectional view showing a first embodiment of a booster pump according to the present invention. It is the principal part expanded sectional view which simplified and expanded the principal part of FIG. It is a principal part expanded sectional view which shows 2nd Embodiment of the pressure | voltage rise pump by this invention. It is a principal part expanded sectional view which shows 3rd Embodiment of the pressure | voltage rise pump by this invention. It is a principal part expanded sectional view which shows 4th Embodiment of the pressure | voltage rise pump by this invention. It is a principal part expanded sectional view which shows 5th Embodiment of the pressure | voltage rise pump by this invention. It is a principal part schematic block diagram which shows one Embodiment of the pressure | voltage rise apparatus by this invention. It is a graph for demonstrating the two-stage compression performed using the pressure | voltage rise apparatus shown in FIG. It is a schematic block diagram which shows one Embodiment of the storage tank for cryogenic fluid by this invention. It is a schematic block diagram which shows other embodiment of the storage tank for cryogenic fluids by this invention. It is a schematic longitudinal cross-sectional view which shows 6th Embodiment of the booster pump for low temperature fluid by this invention. It is XII-XII arrow sectional drawing of FIG. It is a schematic longitudinal cross-sectional view which shows 7th Embodiment of the booster pump for low temperature fluid by this invention. It is a schematic longitudinal cross-sectional view which shows 8th Embodiment of the pressure | voltage rise pump for low temperature fluid by this invention. It is XV-XV arrow sectional drawing of FIG. It is a principal part expanded longitudinal cross-sectional view which shows 9th Embodiment of the booster pump for low temperature fluid by this invention. It is a schematic longitudinal cross-sectional view which shows 10th Embodiment of the booster pump for low temperature fluid by this invention. It is a schematic longitudinal cross-sectional view which shows 11th Embodiment of the booster pump for low temperature fluid by this invention. It is a schematic longitudinal cross-sectional view which shows 12th Embodiment of the booster pump for low temperature fluid by this invention. It is a schematic longitudinal cross-sectional view which shows 13th Embodiment of the booster pump for low temperature fluid by this invention. It is a schematic longitudinal cross-sectional view which shows 14th Embodiment of the booster pump for low temperature fluid by this invention. It is an expanded longitudinal cross-sectional view which shows other embodiment of the bellows applied to the pressure | voltage rise pump for low temperature fluids by this invention. It is an expanded longitudinal cross-sectional view which shows other embodiment of the heat insulation connection part applied to the pressure | voltage rise pump for low temperature fluids by this invention. It is a schematic longitudinal cross-sectional view which shows 15th Embodiment of the booster pump for low temperature fluid by this invention. It is XXV-XXV arrow directional cross-sectional view of FIG. It is a schematic longitudinal cross-sectional view which shows 16th Embodiment of the booster pump for low temperature fluid by this invention.

Hereinafter, a first embodiment of a booster pump (for a cryogenic fluid) according to the present invention will be described with reference to the drawings.
As shown in FIG. 1, a booster pump 1 according to this embodiment is a so-called swash plate type (or swash type), and includes a plurality of (for example, seven) pistons 11, a cylinder block 12, and a cylinder head. 13, a drive shaft 14, and a swash plate (also referred to as “yoke”) 15.

Each piston 11 has a piston head 11a at one end and a piston shoe 11b at the other end, and is a substantially rod-like member having a circular shape in cross section, and is housed in a cylinder 12a (described later) so as to be able to reciprocate. Is.
The piston head 11a is a so-called enlarged portion having an outer diameter larger than the outer diameter of the piston rod 11c connecting the piston head 11a and the piston shoe 11b, and has a flat one end face (FIG. 1). In this case, a low-temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas, liquefied propane gas, etc.) is compressed by the upper end surface in FIG.
Similar to the piston head 11a, the piston shoe 11b is a portion that has a larger outer diameter than the piston rod 11c, that is, a so-called enlarged diameter portion, and a part of the end surface side of the swash plate 15 described later. The end surface of the swash plate 15 is sandwiched between the shoe plate 15a and the retainer ring 15b, and the sliding surface of the thrust roller bearing 16 provided between the shoe plate 15a and the retainer ring 15b is inclined. It is configured to slide along the moving surface P).
The cylinder block 12 has cylinders 12a formed in an annular shape along the longitudinal direction (vertical direction in FIG. 1) and in the same number as the number of pistons 11 in the cylinder block 12a. Each contains one piston 11.
A pressure chamber 12b having an inner diameter larger than the outer diameter of the piston head 11a is provided on one end side (the upper side in FIG. 1) of the cylinder 12a, and the piston head 11a is accommodated in the pressure chamber 12b. It has become.

Here, as shown in FIG. 2 which is a simplified and enlarged view of the main part of FIG. 1 and FIG. 1, bellows 17 are provided in the pressurizing chamber 12b.
This bellows 17 partitions the inner peripheral side (piston 11 side) and the outer peripheral side (cylinder block 12 side) of the pressurizing chamber 12b located on the piston shoe 11b side (lower side in FIG. 1) from the piston head 11a ( One end surface of the piston head 11 a is attached to a surface opposite to the one end surface (the other end surface), and the other end is attached to the inner wall surface of the cylinder block 12.
The bellows 17 is made of, for example, stainless steel or Inconel, which has elasticity at a (very) low temperature.

The cylinder head 13 covers one end surface (the upper end surface in FIG. 1) of the cylinder block 12, and closes the opening end of the cylinder 12a formed inside the cylinder block 12 (that is, the opening end of the pressurizing chamber 12b). Is.
One end face (the lower end face in FIG. 1) of the cylinder head 13, that is, the face opposite to the one end face of the cylinder block 12, is provided with a suction port 13a and a discharge port 13b corresponding to each pressurizing chamber 12b. Are provided. Each of the suction port 13a and the discharge port 13b is provided with a ball-type check valve 18 (a spring is not shown for simplification) so as to control the suction and discharge of the low-temperature fluid. . Each suction port 13 a is provided in communication with a fluid suction passage 19 bored in the cylinder head 13, while each discharge port 13 b is a fluid discharge bored in the cylinder head 13 and the cylinder block 12. It is provided in communication with the path 20. Therefore, the low-temperature fluid guided from the fluid suction path 19 through the suction port 13a into the pressurizing chamber 12b is compressed and pressurized by one end surface of the piston head 11a, and then the fluid discharge path 20 from the discharge port 13b. It is led to the outside through.

The drive shaft 14 transmits a driving force from a driving source (not shown) (for example, an electric motor, an engine, etc.) to the swash plate 15, and can freely rotate inside the other end of the cylinder block 12 via a bearing 21. It is supported.
The swash plate 15 includes a shoe plate 15 a and a retainer ring 15 b, and the sliding surface P of the thrust roller bearing 16 provided between the shoe plate 15 a and the retainer ring 15 b is connected to the longitudinal axis of the cylinder block 12. For example, it is configured to be inclined by 1.43 degrees with respect to the orthogonal axis. Further, a part of the above-described piston shoe 11 b is sandwiched between the retainer ring 15 b and the thrust roller bearing 16.
On the other hand, a thrust roller bearing 22 is also provided between the shoe plate 15 and the cylinder block 12, and axial thrust (longitudinal direction of the cylinder block 12) is received by the thrust roller bearing 22. It is like that.
The shoe plate 15a, the retainer ring 15b, and the thrust roller bearings 16 and 22 rotate together with the drive shaft 14.
Therefore, when the drive shaft 14 is rotated (in one direction) by the drive source, the piston shoe 11b slides along the sliding surface P, and the piston 11 is reciprocated in the cylinder 12 to apply pressure. The low temperature fluid that has flowed into the chamber 12b is successively compressed. In the present embodiment, the stroke of the piston 11 is set to 2 mm.

Reference numeral 23 in FIG. 1 is a communication hole that communicates the pressurizing chamber 12b and the outside of the booster pump 1, and a pipe 24 is connected to the communication hole 23, and in the middle of the pipe 24. An on-off valve 25 is arranged.
When the low-temperature fluid is taken into the pressurizing chamber 12b, the communication hole 23, the pipe 24, and the on-off valve 25 cause the low-temperature fluid existing on the other end surface side of the piston head 11a to flow out from the pressurizing chamber 12b. It is used to reduce the driving resistance of the piston 11 or to let the low temperature fluid that has accumulated in the pressurizing chamber 12b located on the other end surface side of the piston head 11a flow out of the pressurizing chamber 12b. is there.
Therefore, the on-off valve 25 is closed (closed) during the compression stroke or when it is not necessary to let the low temperature fluid flow out of the pressurizing chamber 12b.

According to the booster pump 1 according to the present embodiment, since there is no portion that moves in contact with the inner peripheral surface of the pressurizing chamber 12b (for example, a conventional piston ring), heat generation in the pressurizing chamber 12b is prevented. In addition, it is possible to prevent the low temperature fluid from being heated.
Further, since the inner peripheral side and the outer peripheral side of the pressurizing chamber 12b located on the piston shoe 11b side of the piston head 11a are completely separated by the bellows 17, pressurization is performed from the outer peripheral side of the pressurizing chamber 12b. Leakage of the low temperature fluid to the inner peripheral side of the chamber 12b can be prevented. In other words, the low temperature fluid can be prevented from flowing along the piston rod 11c from the pressurizing chamber 12b side to the piston shoe 11b side. Thereby, the compression efficiency of the booster pump 1 can be improved.

A second embodiment of the booster pump (for cryogenic fluid) according to the present invention will be described with reference to FIG.
In the booster pump 2 in this embodiment, a (thin) wire rod (filler) 31 made of a material that can be used at (very) low temperature such as Teflon (registered trademark) is wound around the outer peripheral surface of the bellows 17. This is different from the first embodiment described above. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 1st Embodiment mentioned above.

As shown in FIG. 3, the wire 31 is wound around the outer surface of the bellows 17 so as to fill the gap between the outer surface of the bellows 17 and the inner peripheral surface of the pressurizing chamber 12 b as much as possible.
The point to be noted here is that the piston 11 is particularly retracted (downward in FIG. 1) so that the outer surface of the wire 31 wound around the outer surface of the bellows 17 does not contact the inner peripheral surface of the pressurizing chamber 12b. To avoid contact when the bellows 17 contracts.

According to the booster pump 2 according to the present embodiment, the gap between the outer surface of the bellows 17 and the inner peripheral surface of the pressurizing chamber 12b is filled, and the dead volume of the pressurizing chamber 12b is reduced, so that the compression efficiency is increased. be able to.
Other functions and effects are the same as the functions and effects of the first embodiment described above, and the description thereof is omitted here.

A third embodiment of a booster pump (for cryogenic fluid) according to the present invention will be described with reference to FIG.
The booster pump 3 in the present embodiment is provided with a spacer (filler) 41 made of a material that can be used at (very) low temperature such as Teflon (registered trademark) on the outer peripheral surface of the bellows 17. This is different from that of the second embodiment described above. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as embodiment mentioned above.

As shown in FIG. 4, each valley portion of the bellows 17 (a portion recessed toward the piston rod 11 c, that is, an additional portion) is formed so as to fill a gap between the outer surface of the bellows 17 and the inner peripheral surface of the pressurizing chamber 12 b as much as possible. A substantially annular spacer 41 in a plan view is disposed on a portion where the distance from the inner peripheral surface of the pressure chamber 12b increases. The cross-sectional shape of the spacer 41 is substantially the same as the cross-sectional shape of the valley portion of the bellows 17 and does not hinder the expansion and contraction of the bellows 17.
The point to be noted here is that the outer surface of the spacer 41 arranged in each valley portion of the bellows 17 does not contact the inner peripheral surface of the pressurizing chamber 12b as described in the second embodiment. In particular, when the piston 11 is retracted (lowered downward in FIG. 1) and the bellows 17 is contracted, the contact is prevented.

Also with the booster pump 3 according to the present embodiment, the gap between the outer surface of the bellows 17 and the inner peripheral surface of the pressurizing chamber 12b is filled, and the dead volume of the pressurizing chamber 12b is reduced, so that the compression efficiency is increased. Can do.
Other functions and effects are the same as the functions and effects of the first embodiment described above, and the description thereof is omitted here.

A fourth embodiment of the booster pump (for cryogenic fluid) according to the present invention will be described with reference to FIG.
In the booster pump 4 in this embodiment, the outer peripheral surface of the bellows 17 is filled with a particulate filler 51 made of a material that can be used at (very) low temperature such as Teflon (registered trademark). And differ from those of the second and third embodiments described above. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as embodiment mentioned above.

As shown in FIG. 5, the gap between the outer surface of the bellows 17 and the inner peripheral surface of the pressurizing chamber 12 b is filled as much as possible to fill the gap between the outer surface of the bellows 17 and the inner peripheral surface of the pressurizing chamber 12 b. Particulate filler 51 is filled.
Further, an outflow prevention ring 52 is attached to one end portion of the bellows 17 so that the filler 51 does not flow out to the one end surface side of the piston head 11a. The ring 52 is formed so that its outer diameter is smaller than the inner diameter of the pressurizing chamber 12b, so that the outer peripheral surface of the ring 52 does not slide along the inner peripheral surface of the pressurizing chamber 12b. Yes.
Each particle constituting the filler 51 is formed such that its outer diameter is larger than the gap between the outer peripheral surface of the ring 52 and the inner peripheral surface of the pressurizing chamber 12b. Further, the filler 51 is filled in an amount that does not hinder the expansion and contraction of the bellows 17.

Also with the booster pump 4 according to the present embodiment, the gap between the outer surface of the bellows 17 and the inner peripheral surface of the pressurizing chamber 12b is filled, and the dead volume of the pressurizing chamber 12b is reduced. Can do.
Other functions and effects are the same as the functions and effects of the first embodiment described above, and the description thereof is omitted here.

A fifth embodiment of a booster pump (for cryogenic fluid) according to the present invention will be described with reference to FIG.
In the booster pump 5 in the present embodiment, a seal member 61 made of a material that can be used at (very) low temperature such as Teflon (registered trademark) is attached to the outer peripheral surface of one end portion of the bellows 17. This is different from the above-described embodiment. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as embodiment mentioned above.

As shown in FIG. 6, a seal member 61 is provided at one end of the bellows 17 to reduce the pressure applied (applied) to the outer peripheral surface of the bellows 17 by the low temperature fluid. The seal member 61 is formed so that the outer diameter thereof is substantially the same as the inner diameter of the pressurizing chamber 12b, and the outer peripheral surface of the ring 52 is slightly in contact with the inner peripheral surface of the pressurizing chamber 12b. It comes to move. However, the seal member 61 does not have a tension like the piston ring which has been regarded as a problem in the past, and the stroke of the piston 11 is largely limited by the bellows 17 (the stroke is small). It does not generate heat like a ring.
Further, the low-temperature fluid that has accumulated in the pressurizing chamber 12b located on the other end surface side of the piston head 11a is temporarily buffered (chamber) (not shown) through the communication hole 23, the pipe 24, and the on-off valve 25 described above. Then, the gas is gasified and used, or is returned to the fluid suction path 19 of the booster pump 5 through a pipe (not shown) and compressed again.

According to the booster pump 5 according to the present embodiment, leakage of low-temperature fluid from the one end surface side of the piston head 11 a to the other end surface side is reduced by the seal member 61, and the pressure applied to the outer peripheral surface of the bellows 17 is reduced. Therefore, a low-pressure bellows that is not severe in strength design can be used, the stroke of the piston 11 can be increased, and the compression efficiency (pump efficiency) can be increased.
Further, the outer peripheral surface of the seal member 61 is configured to move while slightly contacting along the inner peripheral surface of the pressurizing chamber 12b, and heat generation in the pressurizing chamber 12b can be greatly reduced. The heating of the cryogenic fluid can be reduced.
Other functions and effects are the same as the functions and effects of the first embodiment described above, and the description thereof is omitted here.

Next, any one of the above-described boosting pumps (for low-temperature fluid) is used as the low-pressure pump 6L, and any one of the above-described boosting pumps (for low-temperature fluid) is used as the high-pressure pump 6H. The boosting device 6 (for low-temperature fluid) will be described with reference to FIGS.
The low-pressure pump 6L compresses a low-pressure (low bulk modulus) low-temperature fluid to an intermediate pressure, and the bellows uses a low-pressure bellows 17a that can withstand the intermediate pressure and is not severe in strength design. ing.
On the other hand, the high pressure pump 6H compresses an intermediate pressure (high volume modulus) low-temperature fluid compressed by the low pressure pump 6L to a high pressure, and the bellows can withstand high pressure. A high pressure bellows 17b is used.

According to such a pressure increasing device 6, since the low pressure bellows 17a is used in the low pressure pump 6L, the stroke of the piston 11 can be increased, and the low temperature fluid can be easily increased from the low pressure to the intermediate pressure. Further, since the high pressure pump 6H uses the high pressure bellows 17b, the stroke of the piston 11 cannot be increased, but the low temperature fluid can be easily increased from the intermediate pressure to the high pressure. It can be done.
That is, when trying to pressurize a low temperature fluid from low pressure to high pressure all at once using only one booster pump, the high pressure bellows 17b must be used as the bellows, and a large stroke cannot be taken. It was difficult to increase the pressure to a high pressure.
On the other hand, as described above, the low-temperature fluid can be easily boosted to a desired pressure by compressing the low-temperature fluid in two stages using two pumps.

An embodiment of a cryogenic fluid storage tank equipped with a booster pump (for cryogenic fluid) or a booster device (for cryogenic fluid) will be described with reference to FIG.
The storage tank 7 for cryogenic fluid in this embodiment includes a booster pump 71 (for cryogenic fluid) or a booster 72 (for cryogenic fluid), a cryocontainer 73 having an adiabatic vacuum tank 73 a inside, and a cryogenic fluid storage tank 74. The heat exchanger 75 is the main element.
The booster pump 71 or the booster device 72 boosts the low-temperature fluid to a desired pressure. As the booster pump 71, for example, any of the above-described (for low-temperature fluid) booster pumps 1, 2, 3, 4, and 5 is used. As the booster 72, for example, the above-described booster 6 (for low-temperature fluid) can be applied.

The cryogenic container 73 is a container in which the inside is evacuated and a radiation shield plate 76 such as a copper plate is attached to the inner surface thereof. In the heat insulating vacuum chamber 73a of the cryogenic vessel 73, the above-described booster pump 71 or booster device 72, a cryogenic fluid storage tank 74 described later, and a heat exchanger 75 are accommodated.
The low-temperature fluid storage layer 74 stores therein a low-temperature (for example, −253 ° C.) fluid (for example, liquid hydrogen) inside the low-temperature fluid storage layer 74. The pump is guided to a booster pump 71 or a cryogenic fluid booster 72.
One end of the heat exchanger 75 is in contact with the inner surface of the cryogenic vessel 73 (that is, the inner surface of the radiation shield plate 76), and is boosted by the booster pump 71 or the booster 72 and guided through the pipe 78. The fluid is vaporized (gasified) by exchanging heat with the low-temperature container 73 side, and the low-temperature fluid (gas) vaporized by the heat exchanger 75 is supplied to the engine or the like via the pipe 79. ing. The cold recovered by the heat exchanger 75 cools the radiation shield plate 76 described above or is stored in a cold storage material (not shown) housed in the heat insulating vacuum chamber 73.

According to such a cryogenic fluid storage tank 7, as shown in FIG. 9, the booster pump 71 or the booster 72 is disposed in the heat insulating vacuum tank 73 a and outside the cryogenic fluid storage tank 74 ( In other words, the booster pump 71 or the booster device 72 is forcibly cooled to make it difficult to raise the temperature and is generated by the drive source. It is possible to prevent heat from being transferred to the cryogenic fluid stored in the cryogenic fluid storage tank 74 and to prevent the temperature of the cryogenic fluid from rising.
It is desirable that the booster pump 71 or the booster 72 is sufficiently cooled before operation.

Another embodiment of a cryogenic fluid storage tank equipped with a booster pump (for cryogenic fluid) or a booster device (for cryogenic fluid) will be described with reference to FIG.
The storage tank 8 for cryogenic fluid in this embodiment includes a booster pump 81 (for cryogenic fluid) or a booster 82 (for cryogenic fluid), a cryocontainer 83 having an adiabatic vacuum tank 83a therein, and a cryogenic fluid storage tank 84. The heater 85 is the main element.
The booster pump 81 or the booster 82 boosts the low-temperature fluid to a desired pressure. As the booster pump 81, for example, any one of the above-described (for low-temperature fluid) booster pumps 1, 2, 3, 4, and 5 is used. As the booster 82 (for low temperature fluid), for example, the above-described booster 6 (for low temperature fluid) can be applied.

The cryogenic container 83 is a container in which the inside is evacuated and a radiation shield plate 86 such as a copper plate is attached to the inner surface thereof. The above-described booster pump 81 or booster 82 and a later-described cryogenic fluid storage tank 84 are accommodated in the heat insulating vacuum chamber 83a of the cryogenic vessel 83.
The low-temperature fluid storage layer 84 has a low-temperature (for example, −260 ° C.) slush fluid (for example, slush hydrogen: solid hydrogen and liquid hydrogen mixed in a sherbet shape, and has a density higher than that of liquid hydrogen. The low-temperature fluid stored therein is led to the booster pump 81 or the booster 82 via the pipe 87.
When slush hydrogen is stored in the cryogenic fluid storage layer 84, the slush hydrogen is produced by a slush hydrogen production apparatus (not shown) installed in the cryogenic fluid storage layer 84, or outside the cryogenic vessel 83. Manufactured by the slush hydrogen production facility 88 separately prepared.

A mesh (screen) 89 is provided inside the pipe 86. The mesh 89 is configured to pass only a liquid low-temperature fluid (for example, liquid hydrogen) (that is, for example, not to pass solid hydrogen), and thereby the booster pump 81 located on the downstream side. Alternatively, only the liquid low-temperature fluid is supplied to the booster 82, and the booster pump 81 or the booster 82 is prevented from being clogged.
The heater 85 changes (melts) a solid low-temperature fluid (for example, solid hydrogen) into a liquid low-temperature fluid (for example, liquid hydrogen).
Further, it is more preferable that the heat exchanger 75 as described above is provided on the downstream side of the booster pump 81 or the booster 82 and inside the low temperature vessel 83 (or outside the low temperature vessel 83).

  According to such a cryogenic fluid storage tank 8, since the slush-like cryogenic fluid is stored in the cryogenic fluid storage layer 84, it is less likely to evaporate than those in which only the liquid cryogenic fluid is stored. The suction performance of the pump 81 or the booster 82 is improved, and the supply amount of the low-temperature fluid can be increased.

In the embodiment described with reference to FIGS. 7 and 8, the two-stage compression is described using two pumps. However, the present invention is not limited to this, and three pumps are used. It can be used for three-stage compression, or a multistage compression using a larger number of pumps.
Further, such multistage compression does not necessarily require a plurality of pumps, and can be multistage compressed in one pump.

Furthermore, the booster pump according to the present invention can be used not only to pressurize only a low temperature fluid but also to pressurize a fluid having various temperatures from a normal temperature fluid to a high temperature fluid.
Furthermore, it is preferable that the piston rod of the booster pump has a heat insulating vacuum structure that is hollow and evacuated. Thus, by making the piston rod have a hollow structure, the weight of the piston rod can be reduced, and the piston can be pushed up with a low load. In addition, by making the inside of the piston rod in a vacuum state, the piston rod can be insulated, and heat intrusion from the piston rod to the fluid can be reduced.

Next, a sixth embodiment of a cryogenic fluid booster pump according to the present invention will be described with reference to the drawings.
As shown in FIG. 11, the cryogenic fluid booster pump 101 according to the present embodiment is configured with a drive unit 111 and a pump unit 112 driven by the drive unit 111 as main elements.
The drive unit 111 includes a rod 115 and a power transmission unit 116 that transmits power from a drive source (not shown) (for example, an electric motor or an engine) to the rod 115.
The rod 115 is a substantially rod-shaped member that extends downward from the lower end surface of the power transmission unit 116 and has a circular shape in cross section, and a heat insulating connection portion 128 is provided at the lower end thereof.
The power transmission unit 116 reciprocates the rod 115 linearly in the vertical direction (in the direction of the arrow in FIG. 11) with a stroke of 2 mm, for example, by power from a drive source (not shown).

The pump unit 112 includes a piston 121, a piston rod 122, and a cylinder block 123.
The piston 121 includes one piston main body 124 and one or a plurality of (four in this embodiment) piston heads 125 so as to reciprocate within a cylinder 126 formed inside the cylinder block 123. Contained.
The piston main body 124 is a member having a substantially disk shape, and one end portion of the piston rod 122 is connected to the central portion thereof, and the lower end surface of each piston head 125 and the upper surface of the piston main body 124 are connected to the outer peripheral portion thereof. Four rods 127 are provided to connect the end faces.
As shown in FIG. 12, the four piston heads 125 are arranged at equal intervals (90 ° intervals). Each of the piston heads 125 is a member having a substantially disk shape, and low temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas, etc.), liquefied by one end face (the upper end face in FIG. 11). Propane gas or the like can be compressed.

The piston rod 122 is a substantially rod-shaped member having a circular cross-sectional view, and one end portion thereof is connected to the upper end surface of the piston main body 124 as described above, and the other end portion is connected to the heat insulating connecting portion 128. To the tip of the rod 115 (the lower end in FIG. 11).
The heat insulating connecting portion 128 includes a tip portion 128a of a rod 115 having the same form as the inner race of the rolling bearing, a second end portion 128b of the piston rod 122 having the same form as the outer race of the rolling bearing, and the rod 115 A plurality of (four in this embodiment) rolling elements (for example, balls and rollers) 128c disposed between the tip end portion 128a and the other end portion 128b of the piston rod 122 are provided.
As a result, the tip end portion 128a of the rod 115 and the other end portion 128b of the piston rod 122 are connected by point contact or line contact via the rolling element 128c. The heat transfer (heat input) is greatly cut off.
Further, since the piston rod 122 is designed to be as long as possible, even if there is heat transfer (heat input) from the rod 115 to the piston rod 122, the piston rod 122 Heat transfer (heat input) to the piston main body 124 is minimized.

A through hole 123a through which the rod 115 passes is formed at the center of the top of the cylinder block 123, and the inside of the top of the cylinder block 123 communicates with the through hole 123a and accommodates the heat insulating connecting portion 128. A space 129 is formed.
Further, inside the cylinder block 123 positioned below the internal space 129, a cylinder 126 communicating with the internal space 129 through a through hole 123b through which the piston rod 122 passes is provided in the longitudinal direction (vertical direction in FIG. 11). Is drilled along. One end side (the upper side in FIG. 11) of the cylinder 126 is a pressurizing chamber 126a having an inner diameter larger than the outer diameter of the piston head 125, and the piston head 125 can be accommodated in the pressurizing chamber 126a. ing.
The inside of the side wall, the inside of the bottom surface, and the inside of the top surface of the cylinder block 123 have a heat insulating vacuum structure that is hollow and evacuated as indicated by reference numeral 123c.

On the other hand, in the cylinder block 123 located between the pressurizing chamber 126a and the internal space 129, and at positions opposed to the central portion on the one end surface side of the piston head 125, the suctions communicating with the pressurizing chambers 126a, respectively. A port 123d and a discharge port 123e are provided. Each of the suction port 123d and the discharge port 123e is provided with a ball-type check valve 130 so as to control the suction and discharge of the low-temperature fluid.
Each suction port 123d is provided in communication with a fluid suction path 131 drilled in the cylinder block 123, while each discharge port 123e is provided in communication with a fluid discharge path 132 drilled in the cylinder block 123. It has been. Accordingly, the low-temperature fluid guided from the fluid suction passage 131 through the suction port 123d into the pressurizing chamber 126a is compressed by one end face of the piston head 125 and, for example, pressurized (pressurized) to 30 MPa and then discharged. The port 123e is led out of the cylinder block 123 through the fluid discharge path 132.
The low-temperature fluid guided to the outside of the cylinder block 123 through the fluid discharge path 132 is temporarily stored (stored) in the chamber 134 via the pipe 133. The low-temperature fluid stored in the chamber 134 is led to the heat exchanger 136 through the pipe 135 and gasified, and then most of the low-temperature fluid is supplied to a fuel injection device (not shown) through the pipe 137. In addition, a part of the piston body 124 is located inside the cylinder 126 (the other end side of the cylinder 126, that is, on the opposite side to the pressurizing chamber 126a) via a pipe 138 and a pressure regulator (decompressor) 139. The space between the lower surface of the other end and the bottom surface of the cylinder 126).
In the chamber 134, for example, a low-temperature fluid whose pressure has been increased to 30 MPa is stored.
The cylinder 126 is supplied with a gasified low-temperature fluid of, for example, 15 MPa that has been decompressed by the pressure regulator 139.

A bellows (partition member) 140 is provided in each pressurizing chamber 126a. The bellows 140 partitions the inner peripheral side (radially inner side) and the outer peripheral side (radially outer side) of the pressurizing chamber 126a located above the piston head 125 (the side opposite to the piston main body 124). One end of the piston head 125 is attached to the outer peripheral end portion of the piston head 125, and the other end is an inner wall surface of the cylinder block 123 positioned radially outside the suction port 123d and the discharge port 123e. Is attached.
A bellows (partition member) 141 is also provided on the radially outer side of one end of the piston rod 122. The bellows 141 partitions (separates) at one end of the piston rod 122 into an inner peripheral side (piston rod 122 side) and an outer peripheral side (cylinder block 123 side), and one end of the bellows 141 is a piston body. The other end is attached to the inner wall surface of the cylinder block 123.
Each of these bellows 140 and 141 is made of, for example, stainless steel or Inconel, which has elasticity at a (very) low temperature.
In addition, the code | symbol 142,143,144 in FIG. 11 is respectively a planar view cyclic | annular (heat insulation) sealing member.
12 is a cross-sectional view taken along arrow XII-XII in FIG.

  From the above configuration, when the rod 115 of the drive unit 111 linearly reciprocates in the vertical direction, the piston rod 122 coupled to the rod 115 via the heat insulation connecting portion 128 linearly reciprocates with the piston 121 in the vertical direction. The low-temperature fluid sucked from the suction port 123d is compressed by the one end surface of the piston head 125 and pressurized (pressure-increasing), and then passes from the discharge port 123e to the outside of the cylinder block 123 through the fluid discharge path 132. It has been derived.

According to the booster pump 101 for low-temperature fluid according to the present embodiment, there is no portion that moves in contact with the inner peripheral surface of the pressurizing chamber 126a (for example, a conventional piston ring). Heat generation can be prevented and heating of the low-temperature fluid can be prevented.
Moreover, since the inner peripheral side (radially inner side) and the outer peripheral side (radial outer side) of the pressurizing chamber 126a are completely separated by the bellows 140, the pressurizing chamber is separated from the inner peripheral side of the pressurizing chamber 126a. The leakage of the low temperature fluid from the outer peripheral side of 126a (or the outer peripheral side of the pressurizing chamber 126a to the inner peripheral side of the pressurizing chamber 126a) can be prevented, and the compression efficiency of the booster pump 101 for low temperature fluid can be improved. Can be improved.
Furthermore, outside the bellows 140 (radially outside), there is a low-temperature fluid that is gasified by the heat exchanger 136 and whose pressure is adjusted to a predetermined pressure (for example, 15 MPa) by the pressure regulator 139. Therefore, the deformation of the bellows 140 when compressing the low-temperature fluid sucked into the bellows 140 can be reduced, and the life of the bellows 140 can be extended. Reliability can be improved.

  Furthermore, according to the booster pump 101 for low-temperature fluid according to the present embodiment, the internal space of the bellows 140 (the space formed by the inner peripheral surface of the bellows 140, one end surface of the piston head 125, and the upper surface of the pressurizing chamber 126a). Since the low-temperature fluid is compressed inside, the length of the rod 127 connecting the piston head 125 and the piston main body 124 can be shortened. As a result, the length in the longitudinal direction (axial direction) of the pump unit 112 can be shortened, and the length in the longitudinal direction (axial direction) of the entire pump can be shortened. Can be achieved.

Furthermore, when the piston rod 122 is pulled toward the drive unit 111 (upward in FIG. 11), the low-temperature fluid is compressed by one end surface of the piston head 125. That is, the compression force is not applied to the piston rod 122 when compressing the low temperature fluid.
As a result, the diameter of the piston rod 122 can be made smaller than that of the conventional piston rod in which the compression force is applied to the piston rod, so that heat input from the drive source can be reduced and the piston rod 122 can be reduced in weight. This can reduce the weight of the entire pump.

Furthermore, the heat input from the rod 115 to the piston rod 122 can be reduced by the heat insulation connecting portion 128, and the heat input from the drive source can be further reduced.
Furthermore, a piston body 124 is provided between the piston rod 122 and the piston head 125, and heat from the piston rod 122 reaches the piston head 125 after passing through the piston body 124. The amount of heat can be further reduced.
Furthermore, since the rod 115 connected to the power transmission unit 116 extends on the same side as the side where the suction port 123d and the discharge port 123e are arranged (upper side in FIG. 11), the longitudinal direction (axial direction) of the pump unit 112 ) Can be shortened, and the length of the entire pump in the longitudinal direction (axial direction) can be shortened, so that the pump can be reduced in size and weight.

A seventh embodiment of the booster pump for low temperature fluid according to the present invention will be described with reference to FIG.
The cryogenic fluid booster pump 202 according to the present embodiment is a so-called swash plate type (or swash type), and is composed mainly of a drive unit 261 and a pump unit 262 driven by the drive unit 261. Is.
In addition, the same code | symbol is attached | subjected to the component same as 6th Embodiment mentioned above.

The drive unit 261 includes a rod 265 and a power transmission unit 266 that transmits power from a drive source (not shown) (for example, an electric motor or an engine) to the rod 265.
The rod 265 is a substantially rod-shaped member that extends downward from the lower end surface of the power transmission unit 266 and has a circular shape in cross section.
The power transmission unit 266 rotates the rod 265 in one direction (the direction of the arrow in FIG. 13) by power from a drive source (not shown).

The pump unit 262 includes one or a plurality (four in this embodiment) of pistons 271, a swash plate (also referred to as “yoke”) 272, and a cylinder block 273.
Each piston 271 has a piston head 271a at one end and a piston shoe 271b at the other end, and is a substantially rod-like member having a circular shape in cross section, and is housed in a cylinder 276 so as to be able to reciprocate. .
The piston head 271a is a so-called expanded portion having an outer diameter larger than the outer diameter of the piston rod 271c that connects the piston head 271a and the piston shoe 271b, and has a flat end face (FIG. 13). In this case, a low-temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas, etc.), liquefied propane gas, or the like is compressed by the upper end surface.
Similar to the piston head 271a, the piston shoe 271b is a so-called enlarged portion having an outer diameter larger than the outer diameter of the piston rod 271c, and its end surface (the lower surface in FIG. 13) The swash plate 272 having an inclination angle is configured to slide along the sliding surface P.

The cylinder block 273 has pressurizing chambers 126a bored in the longitudinal direction (vertical direction in FIG. 13) by the same number as the number of pistons 271 inside, and in each pressurizing chamber 126a. Each includes one piston head 271a.
As shown in FIG. 13, the piston shoe 271 b and the swash plate 272 are accommodated on the other end side (lower side in FIG. 13) of the cylinder 276.
A through hole 123a through which the rod 265 passes is formed at the center of the cylinder block 273, and the inside of the side wall, the inside of the bottom surface, and the inside of the top surface of the cylinder block 123 are hollow as indicated by reference numeral 123c. It is a heat insulating vacuum structure that is evacuated with a vacuum.

On the other hand, a suction port 123d and a discharge port 123e communicating with each pressurizing chamber 126a are provided inside the top of the cylinder block 273 and at a position facing the central portion on one end surface side of the piston head 271a. Each of the suction port 123d and the discharge port 123e is provided with a ball-type check valve 130 so as to control the suction and discharge of the low-temperature fluid.
Each suction port 123d is provided in communication with a fluid suction path 131 drilled in the cylinder block 123, while each discharge port 123e is provided in communication with a fluid discharge path 132 drilled in the cylinder block 123. It has been. Therefore, the low-temperature fluid guided from the fluid suction passage 131 through the suction port 123d into the pressurizing chamber 126a is compressed by one end face of the piston head 271a and, for example, pressurized (pressurized) to 30 MPa and then discharged. It is led out of the cylinder block 273 through the fluid discharge path 132 from the port 123e.
The low-temperature fluid guided to the outside of the cylinder block 273 through the fluid discharge path 132 is temporarily stored (stored) in the chamber 134 via the pipe 133. The low-temperature fluid stored in the chamber 134 is led to the heat exchanger 136 through the pipe 135 and gasified, and most of the low-temperature fluid is supplied to a fuel injection device (not shown) through the pipe 137. In addition, a part of the inside of the pressurizing chamber 126a via the pipe 138 and the pressure regulator (decompressor) 139 (that is, the space on the other end surface side of the piston head 271a located on the side opposite to the bellows 140). To be guided to.
In the chamber 134, for example, a low-temperature fluid whose pressure has been increased to 30 MPa is stored.
The pressurized chamber 126a is supplied with a gasified low temperature fluid of, for example, 15 MPa, decompressed by the pressure regulator 139.

A bellows (partition member) 140 is provided in each pressurizing chamber 126a. The bellows 140 partitions an inner peripheral side (radially inner side) and an outer peripheral side (radially outer side) of the pressurizing chamber 126a located above the piston head 271a (the side opposite to the piston rod 271c). One end of the piston head 271a is attached to the outer peripheral end of the piston head 271a, and the other end is the inner wall surface of the cylinder block 273 located radially outside the suction port 123d and the discharge port 123e. Is attached to.
A bellows (partition member) 280 is also provided on the radially outer side of one end of the piston rod 271c. The bellows 280 partitions (separates) the piston rod 271c into an inner peripheral side (piston rod 271c side) and an outer peripheral side (cylinder block 273 side) at one end of the piston rod 271c. The other end surface of 271b (the upper surface in FIG. 13) is attached to the outer peripheral end portion, and the other end is attached to the inner wall surface of the cylinder block 273.
Each of these bellows 140, 280 is made of, for example, stainless steel or Inconel having elasticity at (very) low temperatures.
Note that reference numerals 142, 143, and 144 in FIG. 13 are annular (thermal insulating) seal members in plan view, and reference numerals 281 and 282 are thrust roller bearings.

  From the above configuration, when the rod 265 is rotated (in one direction) by the drive source, the piston shoe 271b slides along the sliding surface P via the thrust bearing 281 and the piston 271 is moved in the cylinder 276. The low-temperature fluid that has been reciprocated and has flowed into the pressurizing chamber 126a is successively compressed. In the present embodiment, the stroke of the piston 271 is set to 2 mm, for example.

According to the booster pump 202 for low-temperature fluid according to the present embodiment, there is no portion that moves in contact with the inner peripheral surface of the pressurizing chamber 126a (for example, a conventional piston ring). Heat generation can be prevented and heating of the low temperature fluid can be prevented.
Further, since the inner peripheral side (radially inner side) and the outer peripheral side (radial outer side) of the pressurizing chamber 126a are completely separated by the bellows 140, the pressurizing chamber is separated from the inner peripheral side of the pressurizing chamber 126a. The leakage of the low temperature fluid from the outer peripheral side of 126a (or the outer peripheral side of the pressurizing chamber 126a to the inner peripheral side of the pressurizing chamber 126a) can be prevented, and the compression efficiency of the booster pump 202 for low temperature fluid can be improved. Can be improved.
Further, outside the bellows 140 (outside in the radial direction), a low-temperature fluid that is gasified by the heat exchanger 136 and whose pressure is adjusted to a predetermined pressure (for example, 15 MPa) by the pressure regulator 139 exists. Therefore, deformation of the bellows 140 when compressing the low-temperature fluid sucked into the bellows 140 can be reduced, and the life of the bellows 140 can be extended. Reliability can be improved.

  Furthermore, according to the cryogenic fluid booster pump 202 according to the present embodiment, the internal space of the bellows 140 (the space formed by the inner peripheral surface of the bellows 140, one end surface of the piston head 271a, and the upper surface of the pressurizing chamber 126a). Since the low-temperature fluid is compressed inside, the length of the piston rod 271c connecting the piston head 271a and the piston shoe 271b can be shortened. As a result, the length of the pump portion 262 in the vertical direction (axial direction) can be shortened, and the length of the entire pump in the vertical direction (axial direction) can be shortened. Can be achieved.

Furthermore, when the rod 265 is rotated in one direction (the direction of the arrow in FIG. 13), the low temperature fluid is compressed by one end surface of the piston head 271a. That is, the compression force is not applied to the rod 265 when compressing the low-temperature fluid.
As a result, the diameter of the rod 265 can be made smaller than that of the conventional piston rod type in which a compressive force is applied to the rod, so that heat input from the drive source can be reduced and the rod 265 can be reduced in weight. This can reduce the weight of the entire pump.
Furthermore, since the rod 265 connected to the power transmission unit 266 extends on the same side as the side where the suction port 123d and the discharge port 123e are disposed (upper side in FIG. 13), the longitudinal direction (axial direction) of the pump unit 262 ) Can be shortened, and the length of the entire pump in the longitudinal direction (axial direction) can be shortened, so that the pump can be reduced in size and weight.

  In the above-described embodiment, a four-cylinder type having four pistons and four cylinders has been described. However, the present invention is not limited to this, and for example, a single cylinder, a two-cylinder, or a three-cylinder Alternatively, a configuration with five or more cylinders may be employed.

Further, the thrust roller bearing 282 described in the seventh embodiment is not limited to one supporting the central portion of the lower surface of the swash plate 272 as shown in FIG. It can also be supported by a plurality of thrust roller bearings arranged in the direction.
Furthermore, it is preferable that the angle of the swash plate 272 is configured to be changeable by using an actuator or the like, that is, configured to be a variable capacity type. As a result, the pump discharge amount can be changed only by changing the angle of the swash plate 272 without changing the drive rotational speed of the pump.

  Furthermore, in the above-described embodiment, the ball-type check valve 130 is provided in each of the suction port 123d and the discharge port 123e, but the present invention is not limited to this, and can be found in a DOHC such as an internal combustion engine. Such a forced drive type may be used, or a configuration such as a reed valve, a poppet valve, or the like may be employed.

Furthermore, in the sixth embodiment or the seventh embodiment described above, the low-temperature fluid gasified by the heat exchanger 136 is supplied to the outside of the bellows 140, 280. However, the present invention is not limited to this, and the space in which the gasified low-temperature fluid has been supplied can be in a vacuum state.
That is, the space between the bellows 140, 280 and the cylinder block 123, 273 is evacuated, and the cylinder block 123, 273 is compressed by the heat inside the bellows 140, 280 (that is, inside the bellows 140, 280). The heat of the low temperature fluid) is prevented from being transmitted.
Thereby, while the temperature rise of the cylinder blocks 123 and 273 is suppressed, the temperature rise of the low-temperature fluid flowing into the pressurizing chamber is suppressed.
At this time, the pipe 138 and the pressure regulator 139 shown in FIGS. 11 and 13 are omitted.

Furthermore, in the above-described sixth embodiment, the piston main body, piston head, and the like that are housed in the cylinder and reciprocate in the cylinder do not collide with the inner wall surface (cylinder wall) of the cylinder. More preferably, a guide member is provided between the piston rod 122 and the cylinder block 123 or between the connecting member 124 and the cylinder 126.
As the guide member, for example, a linear bearing disposed between the piston rod 122 and the cylinder block 123, between the outer peripheral surface of the connecting member 124 and the inner wall surface of the cylinder 126, or downward from the lower end surface of the connecting member 124. And a cylindrical protrusion protruding in the center of the bottom surface of the cylinder 126 is guided in a cylindrical recess (dent).
As a result, the reciprocating members such as the piston main body and the piston head reciprocate without shaking or vibrating in the cylinder, and the reciprocating member can be prevented from colliding with the inner wall surface of the cylinder. In addition, the reciprocating member can be smoothly driven with minimal power.

Furthermore, in each of the sixth embodiment or the seventh embodiment described above, the space in which the low-temperature fluid gasified in these embodiments is supplied can be in a vacuum state.
Thereby, while the temperature rise of a cylinder block is suppressed, the temperature rise of the low-temperature fluid which flows in into a pressurization chamber will be suppressed.
At this time, the piping 138 and the pressure regulator 139 shown in FIGS. 11 and 13 are omitted.

Furthermore, in the above-described sixth embodiment, it is more preferable that a space in which the inside of the piston rod 122 and the cylinder block 123 is in a vacuum state is formed.
For example, the space on the inner peripheral side and the space on the outer peripheral side of the piston rod 122 are separated between the lower surface of the other end 128b of the piston rod 122 and the upper surface of the bottom of the internal space 129 shown in FIG. A bellows).
That is, the space between the cylinder block 123 and the piston rod 122 is in a vacuum state, and the heat from the piston rod 122 (that is, the heat that has entered the piston rod 122 side from the drive unit 111 side) into the cylinder block 123. ) Is prevented from being transmitted.
Thereby, while the temperature rise of the cylinder block 123 is suppressed, the temperature rise of the low temperature fluid which flows in into the pressurization chamber 126a will be suppressed.

Next, an eighth embodiment of the booster pump for low temperature fluid according to the present invention will be described with reference to the drawings.
As shown in FIG. 14, the cryogenic fluid booster pump 301 according to the present embodiment includes a drive unit 311 and a pump unit 312 driven by the drive unit 311 as main elements.
The drive unit 311 includes a cam 313, a reciprocating unit 314, a linear bearing 315, an urging member 316, and a casing 317 that accommodates these elements.
The cam 313 is an arc cam (convex cam) having a maximum lift (maximum lift) of 2 mm, for example, fixed to a drive shaft 318 of a drive source (not shown) (for example, an electric motor or an engine). It rotates in one direction with the drive shaft 318 which rotates by being driven.

The reciprocating part 314 is a substantially cylindrical member in which an internal space is formed. The reciprocating part 314 has a rolling bearing (bearing) 319 in the internal space and has a circular shape in cross-section from the lower end surface downward. A substantially rod-shaped rod 320 is extended.
The rolling bearing 319 includes an inner race (inner ring) 319a, an outer race (outer ring) 319b, and a plurality of rolling elements (eg, balls and rollers) 319c disposed between the inner race 319a and the outer race 319b. It has. The inner race 319a is attached to a shaft 314a projecting in the internal space of the reciprocating portion 314, and the outer race 319b has a cam that is in line contact with the outer surface of the rotating cam 313. It rotates with 313.

The linear bearing 315 guides the radially outer peripheral surface of the reciprocating part 314 so that the reciprocating part 314 linearly reciprocates in the vertical direction. And it is attached to the side inner wall surface of the casing 317. Inside the linear bearing 315, a plurality of rolling elements (for example, balls and rollers) 315a are arranged so that the reciprocating motion of the reciprocating portion 314 in the vertical direction smoothly (smoothly). It has come to be.
In addition, as a material of the linear bearing 315, resin, titanium, a ceramic etc. can be mentioned, for example.
The urging member 316 is attached to the upper inner wall surface of the casing 317, and is disposed on the upper side of the reciprocating part 314 to urge the reciprocating part 314 downward, that is, the outer race 319b of the rolling bearing 319. For example, a compression spring is used to bias the outer surface toward the outer surface of the cam 313.
The casing 317 is a substantially cylindrical member in which an internal space for accommodating the cam 313, the reciprocating part 314, the linear bearing 315, and the biasing member 316 is formed, and is disposed above the pump part 312. ing.

  From the above configuration, when the drive source is driven and the cam 313 rotates together with the drive shaft 318, the rolling bearing 319 whose outer surface is pressed against the outer surface of the cam 313 linearly moves up and down together with the reciprocating unit 314. The rod 320 is also reciprocated linearly in the vertical direction.

The pump unit 312 includes a piston 321, a piston rod 322, and a cylinder block 323.
The piston 321 includes a piston main body 324 and a piston head 325, and is accommodated in a cylinder 326 formed inside the cylinder block 323 so as to reciprocate.
The piston main body 324 is a bottomed hollow member having a generally cup shape, and a piston head 325 is disposed at one end (the upper end in FIG. 14) and the other end (bottom) central portion. A through hole 324a through which one end of the piston rod 322 passes is formed, and one end of the piston rod 322 is attached via a heat insulating material 327. Further, the inside of the side wall of the piston main body 324 has a heat insulating vacuum structure that is hollow and evacuated as indicated by reference numeral 324b.
The piston head 325 is a member having an annular shape (doughnut shape) in a plan view and having a through hole 325a through which a piston rod 322 and a partition wall 334, which will be described later, penetrate at the center, and one flat end surface (upper side in FIG. 14). The low-temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas, liquefied propane gas, etc.) is compressed by the end face.

The piston rod 322 is a substantially rod-shaped member having a circular cross-sectional view, and one end thereof is attached to the center of the other end of the piston main body 324 via the heat insulating material 327 as described above. The end portion is connected to the tip end portion (the lower end portion in FIG. 14) of the rod 320 via the heat insulation connecting portion 328.
The heat insulation connecting portion 328 includes a tip portion 328a of a rod 320 having the same form as the inner race of the rolling bearing, a second end portion 328b of a piston rod 322 having the same form as the outer race of the rolling bearing, and the rod 320 A plurality of (four in this embodiment) rolling elements (for example, balls and rollers) 328c disposed between the tip 328a and the other end 328b of the piston rod 322 are provided.
As a result, the tip end portion 328a of the rod 320 and the other end portion 328b of the piston rod 322 are connected by point contact or line contact via the rolling element 328c, so that the rod 320 is moved to the piston rod 322. The heat transfer (heat input) is greatly cut off.
In addition, since one end of the piston rod 322 and the center of the other end of the piston main body 324 are connected via a heat insulating material 327, heat transfer from the rod 320 to the piston rod 322 ( Even if there is heat input), the heat transfer (heat input) from the piston rod 322 to the piston main body 324 is blocked by the heat insulating material 327.

A through hole 323a through which the rod 320 passes is formed in the central portion of the top of the cylinder block 323, and the inside of the top of the cylinder block 323 communicates with the through hole 323a and accommodates the heat insulating connecting portion 328. A space 329 is formed.
A cylinder 326 communicating with the internal space 329 via a through hole 323b through which the piston rod 322 passes is disposed in the cylinder block 323 positioned below the internal space 329 in the longitudinal direction (vertical direction in FIG. 14). Is drilled along. One end side (the upper side in FIG. 14) of the cylinder 326 is a pressurizing chamber 326a having an inner diameter larger than the outer diameter of the piston head 325, and the piston head 325 can be accommodated in the pressurizing chamber 326a. ing.
As indicated by reference numeral 323c, the inside of the side wall, the inside of the bottom surface, and the inside of the top surface of the cylinder block 323 have a heat insulating vacuum structure that is hollow and evacuated.

On the other hand, in the cylinder block 323 located between the pressurizing chamber 326a and the internal space 329 and at a position facing the one end surface side peripheral end of the piston head 325, a suction port communicating with the pressurizing chamber 326a. 323d and a discharge port 323e are provided. Each of the suction port 323d and the discharge port 323e is provided with a poppet type check valve (or a ball type check valve, a reed valve, a valve by forcible drive) 330 having a valve body 330a and a spring 330b. Suction and discharge are controlled.
The suction port 323d is provided in communication with the fluid suction path 331 drilled in the cylinder block 323, while the discharge port 323e is provided in communication with the fluid discharge path 332 drilled in the cylinder block 323. Yes. Therefore, the low-temperature fluid introduced into the pressurizing chamber 326a from the fluid suction path 331 through the suction port 323d is compressed by one end surface of the piston head 325 and, for example, pressurized (pressurized) to 30 MPa and then discharged. The port 323 e is led out of the cylinder block 323 through the fluid discharge path 332.
The low-temperature fluid guided to the outside of the cylinder block 323 through the fluid discharge path 332 is temporarily stored in the chamber C through the pipe 333 and then supplied to a fuel injection device (not shown) through the pipe 335. It has become.
In the chamber C, for example, a low-temperature fluid whose pressure is increased to 30 MPa is stored.

  A partition wall 334 is provided between the piston rod 322 and the piston 321 so as to cover the outer surface of the shaft portion of the piston rod 322. The inside of the partition wall 334 has a heat-insulating vacuum structure that is hollow and evacuated as indicated by reference numeral 334 a, thereby preventing radiant heat from the piston rod 322 from being transmitted to the piston 321. Yes.

A bellows (partition member) 336 is provided in the pressurizing chamber 326a. The bellows 336 includes an inner peripheral side (piston 321 side) and an outer peripheral side (cylinder block 323 side) of the pressurizing chamber 326a located on the piston body 324 side (lower side in FIG. 14) with respect to the piston head 325. One end of the piston head 325 is attached to a surface opposite to the one end surface (the other end surface), and the other end is attached to the inner wall surface of the cylinder block 323.
A bellows (partition member) 337 is also provided on the radially outer side of the partition wall 334 located above one end surface of the piston head 325. The bellows 337 partitions (separates) the upper side of the cylinder 326 into an inner peripheral side (piston rod 322 side) and an outer peripheral side (cylinder block 323 side), and one end of the bellows 337 is a part of the piston head 325. The other end is attached to the inner wall surface of the cylinder block 323 while being attached to the end face.
Each of these bellows 336 and 337 is made of, for example, stainless steel or Inconel, which has elasticity at a (very) low temperature.
15 is a cross-sectional view taken along arrow XV-XV in FIG. 14, and an imaginary line (two-dot chain line) in FIG. 15 indicates a bellows 337.
Further, reference numerals 338, 339, 340, and 341 in FIG. 14 are annular (thermal insulating) seal members in plan view, respectively.

  From the above configuration, when the rod 320 of the drive unit 311 linearly reciprocates in the vertical direction, the piston rod 322 coupled to the rod 320 via the heat insulating connection unit 328 linearly reciprocates in the vertical direction together with the piston 321. The low-temperature fluid sucked from the suction port 323d is compressed by the one end surface of the piston head 325 and pressurized (pressure-increasing), and then passes from the discharge port 323e through the fluid discharge path 332 to the outside of the cylinder block 323. It has been derived.

According to the booster pump 301 for low-temperature fluid according to the present embodiment, the low-temperature fluid is compressed by one end face of the piston head 325 by pulling the piston rod 322 toward the drive unit 311 (upward in FIG. 14). It has become. That is, the compression force is not applied to the piston rod 322 when the low temperature fluid is compressed.
As a result, the diameter of the piston rod 322 can be made smaller than that of a conventional piston rod in which a compression force is applied to the piston rod (for example, when the piston rod 322 is made of Inconel, the diameter of the piston rod 322 is 8 mm, for example, Therefore, the heat input from the drive source can be reduced, the weight of the piston rod 322 can be reduced, and the weight of the entire pump can be reduced.

Further, since the compression force is not applied to the piston rod 322 when compressing the low temperature fluid, the diameter of the piston head 325 can be increased (for example, the diameter can be set to 100 mm). That is, in the conventional pump in which the compression force is applied to the piston rod, the diameter of the piston head is limited to, for example, a diameter of 40 mm in order to avoid buckling of the piston rod. Therefore, in the conventional pump, for example, five cylinders are required to secure the flow rate of the low-temperature fluid. In the pump of the present invention, the diameter of the piston head 325 can be set to, for example, a diameter of 100 mm. Therefore, a sufficient flow rate can be secured even with a single cylinder.
Thereby, in the pump of this invention, while being able to simplify the structure of a pump, the weight reduction and diameter reduction of the whole pump can be achieved.

Furthermore, since the cam 313 and the rolling bearing 319 are configured to be in line contact, heat input from the drive source can be further reduced.
Furthermore, the heat input from the rod 320 to the piston rod 322 can be reduced by the heat insulating connecting portion 328, and the heat input from the driving source can be further reduced.
Furthermore, even if there is heat transfer (heat input) from the rod 320 to the piston rod 322, the heat input from the piston rod 322 to the piston main body 324 can be prevented by the heat insulating material 327.
Furthermore, a piston main body 324 is provided between the piston rod 322 and the piston head 325, and heat from the piston rod 322 reaches the piston head 325 after passing through the piston main body 324. The amount of heat can be further reduced.
Furthermore, since the inside of the piston main body 324 has a heat insulating vacuum structure that is hollow and evacuated, the amount of heat input can be further reduced.
Thereby, the amount of heat input to the piston head 325 can be reduced, and gasification (boil-off) of the low-temperature fluid compressed by the one end surface of the piston head 325 can be reduced.

  Further, according to the booster pump 301 for low-temperature fluid according to the present embodiment, there is no portion that moves in contact with the inner peripheral surface of the pressurizing chamber 326a (for example, a conventional piston ring), so the pressurizing chamber 326a Heat generation in the inside can be prevented, and the low temperature fluid can be prevented from being heated.

A ninth embodiment of the booster pump for low temperature fluid according to the present invention will be described with reference to FIG.
The booster pump 402 for low-temperature fluid according to this embodiment is different from that of the eighth embodiment described above in that a piston head 325 is directly attached to one end of a piston rod 322. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 8th Embodiment mentioned above.

As shown in FIG. 16, in the cryogenic fluid booster pump 402 according to this embodiment, the length of the piston rod 322 is about ¼ of that of the eighth embodiment, and one end of the piston rod 322 is made of a heat insulating material 327. Is directly attached to a through-hole 325b formed at the center of the piston head 325. Therefore, in the present embodiment, the piston body 324, the partition wall 334, and the cylinder 326 located below the bellows 336 in the eighth embodiment are omitted, and the vertical direction of the pump as a whole (the vertical direction in the drawing). The length of is shortened.
In addition, it seems that the heat input from a drive source becomes a problem by omitting the piston main body 324 and the partition 334. However, as described above, the cam 313 and the rolling bearing 319 are configured to be in line contact, and the tip end portion 328a of the rod 320 and the other end portion 328b of the piston rod 322 are connected by the heat insulating connection portion 328. In addition, since it is configured to be connected by point contact or line contact via the rolling element 328c, heat input from the driving source hardly poses a problem.
Rather than that, there is a very great merit that the length in the vertical direction of the pump part 412 can be significantly shortened, and this makes it possible to reduce the length in the vertical direction of the entire pump, The pump can be downsized.

A tenth embodiment of a booster pump for cryogenic fluid according to the present invention will be described with reference to FIG.
The booster pump 503 for low-temperature fluid according to the present embodiment performs the first compression (first stage compression) on the outer peripheral edge side of the piston head 525 and the second compression (second stage compression) on the inner peripheral edge side of the piston head 525. ) Is different from that of the eighth embodiment described above. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 8th Embodiment mentioned above.

As shown in FIG. 17, in the booster pump for low-temperature fluid 503 according to this embodiment, the first compression is performed on the outer peripheral side of the piston head 525, and the second compression is performed on the inner peripheral side of the piston head 525. In addition, the drive unit 311 and the low-pressure chamber 534 are provided in the cylinder block 523.
The piston 521 in this embodiment includes a piston main body 524 and a piston head 525, and is housed in a cylinder 326 formed inside the cylinder block 523 so as to be able to reciprocate.
The piston head 525 has a first compression surface 525a on one end face on the outer peripheral edge side (the upper end face in FIG. 17), and a second compression surface 525b on one end face on the inner peripheral edge side. The low-temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas, liquefied propane gas, etc.) is compressed by these flat compression surfaces 525a and 525b.

Accordingly, the low-temperature fluid guided from the fluid suction path 331 through the low-pressure side suction port P1 into the pressurizing chamber 326a is compressed by the first compression surface 525a of the piston head 525 and pressurized to, for example, 5 MPa ( After the pressure is increased, the pressure is once accumulated in the low-pressure chamber 534 through the first communication path (flow path connecting the low-pressure side discharge port P2 and the low-pressure chamber 534) from the low-pressure side discharge port P2. It has become.
The low-temperature fluid stored in the low-pressure chamber 534 is guided from the low-pressure chamber 534 to the high-pressure side suction port P3 through the second communication path (a flow path connecting the low-pressure chamber 534 and the high-pressure side suction port P3). Then, it is guided into the pressurizing chamber 326a. The low-temperature fluid introduced into the pressurizing chamber 326a is compressed by the second compression surface 525b of the piston head 525, and is pressurized (pressurized) to 30 MPa, for example, and then the fluid discharge path from the high-pressure side discharge port P4. It is led out of the cylinder block 523 through 332. The low-temperature fluid led to the outside of the cylinder block 523 is temporarily stored in the chamber C via the pipe 333 and then supplied to a fuel injection device (not shown) via the pipe 335.

According to the booster pump 503 for low-temperature fluid according to the present embodiment, the low-temperature fluid is temporarily pressurized to, for example, 5 MPa by the first compression surface 525a of the piston head 525, and then is compressed by the second compression surface 525b of the piston head 525. Further pressurization is performed to pressurize the low temperature fluid to a desired pressure (for example, 30 MPa).
That is, in this embodiment, instead of trying to pressurize the low temperature fluid from low pressure to high pressure at once, pressurize the low temperature fluid to a desired pressure (high pressure) after pressurizing the low temperature fluid to an intermediate pressure. Stage compression is adopted.
Thereby, since the stroke of the piston 521 (that is, the maximum lift of the cam 313) can be reduced, the longitudinal length of the pump portion 512 can be further shortened, and the longitudinal length of the entire pump can be reduced. Further reduction can be achieved, and the pump can be further reduced in size.
Further, as the stroke of the piston 521 decreases, the expansion / contraction rate of the bellows 336, 337 can be reduced (that is, the expansion / contraction range can be reduced), so that the life of the bellows 336, 337 can be extended. It is possible to improve the reliability of the pump.
Other functions and effects are the same as the functions and effects of the eighth embodiment described above, and a description thereof is omitted here.

An eleventh embodiment of a cryogenic fluid booster pump according to the present invention will be described with reference to FIG.
The booster pump 604 for low-temperature fluid according to the present embodiment is the same as that of the eighth embodiment described above in that the precooling layer 630 is provided inside the adiabatic vacuum structure 323c of the cylinder block 623 constituting the pump unit 612. And different. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 8th Embodiment mentioned above.

  As shown in FIG. 18, the cryogenic fluid booster pump 604 according to the present embodiment is provided with a precooling layer 630 inside the side wall, inside the bottom surface, and inside the top surface of the cylinder block 623. A coolant inlet pipe 631 and a coolant outlet pipe 632 are connected to the precooling layer 630, and a coolant (for example, liquid hydrogen, liquid nitrogen, liquefaction, etc.) supplied from the coolant inlet pipe 631 into the precooling layer 630. A low-temperature fluid such as carbon dioxide gas, liquefied natural gas, or liquefied propane gas) is led out of the cylinder block 623 through the coolant outlet pipe 632.

By providing such a pre-cooling layer 630, the entire pump can be sufficiently cooled before the pump is started, so that gasification (boil-off) of the low-temperature fluid supplied to the low-temperature fluid booster pump 604 is reduced. Can do.
Further, since the precooling layer 630 serves as a heat insulating layer even during the pump operation, gasification (boil-off) of the low temperature fluid can be reduced even during the pump operation.
Other functions and effects are the same as those of the above-described eighth embodiment, and thus description thereof is omitted here.

A twelfth embodiment of a booster pump for low temperature fluid according to the present invention will be described with reference to FIG.
The cryogenic fluid booster pump 705 according to the present embodiment is different from that of the eleventh embodiment described above in that a bellows 737 is provided instead of the bellows 337. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 11th Embodiment mentioned above.

As shown in FIG. 19, the bellows (partition member) 737 of the cryogenic fluid booster pump 705 according to this embodiment is a pressurizing chamber 326 a located on the piston body 324 side (lower side in FIG. 19) with respect to the piston head 325. And one end of the bellows 336 is attached to a surface (the other end surface) opposite to the one end surface of the piston head 325, and the other end is the upper surface of the tongue portion of the partition wall 334. Is attached to.
The bellows 737 is made of, for example, stainless steel or inconel having elasticity at (very) low temperature, like the bellows 336 and 337 described above.

Thus, by providing the bellows 737 on the same side as the bellows 336, that is, on the side opposite to one end surface (compression surface) of the piston head 325, the length in the pump height direction (vertical direction in the figure) is shortened. The pump can be downsized.
In addition, since the area of the compression surface of the piston head 325 is larger than that of the eleventh embodiment, more low-temperature fluid can be compressed at a time, and the pump can be made more efficient (higher capacity). ).
Other functions and effects are the same as the functions and effects of the eleventh embodiment described above, and a description thereof is omitted here.
In addition, the code | symbol 712 in a figure has shown the pump part.

A thirteenth embodiment of a cryogenic fluid booster pump according to the present invention will be described with reference to FIG.
The cryogenic fluid booster pump 806 according to the present embodiment is different from that of the twelfth embodiment described above in that a bellows 837 is further provided. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 12th Embodiment mentioned above.

As shown in FIG. 20, the bellows 737 is provided with another bellows (partition member) 837 on the other end side (lower side in the drawing) of the low-temperature fluid booster pump 806 according to this embodiment. One end of the bellows 837 is attached to the lower surface of the tongue portion of the partition wall 334, and the other end is attached to the upper surface of the inner wall of the other end portion of the piston body 324. The bellows 837 allows the space between the lower surface of the tongue portion of the partition wall 334 and the upper surface of the inner wall of the other end of the piston body 324 to be on the inner peripheral side (piston rod 322 side) and outer peripheral side (cylinder block 323 side). It is designed to be partitioned (separated).
The bellows 837 is made of, for example, stainless steel or Inconel that has elasticity at a (very) low temperature, like the bellows 336, 337, and 737 described above.

By providing such a bellows 837, the pressure in the space on the piston rod 322 side partitioned by the sealing member 341 and the bellows 837 described above is maintained at a substantially atmospheric pressure. , 837 can reduce the difference (pressure difference) between the pressure on the inner peripheral side and the pressure on the outer peripheral side, can extend the life of these bellows 336, 737, 837, and can improve the reliability of the pump. Can be improved.
Other functions and effects are the same as the functions and effects of the eleventh embodiment described above, and a description thereof is omitted here.
In addition, the code | symbol 812 in a figure has shown the pump part.

A fourteenth embodiment of a cryogenic fluid booster pump according to the present invention will be described with reference to FIG.
The cryogenic fluid booster pump 907 according to the present embodiment is different from that of the eighth embodiment described above in that a pressurized fluid supply unit 930 is provided. Since other components are the same as those in the above-described embodiment, description of these components is omitted here.
In addition, the same code | symbol is attached | subjected to the member same as 8th Embodiment mentioned above.

  As shown in FIG. 21, a booster fluid supply unit 930 is provided in the cryogenic fluid booster pump 907 according to the present embodiment. The pressurizing fluid supply unit 930 includes the inside of the chamber C and the inside of the cylinder 326 (on the other end side of the cylinder 326, that is, on the opposite side to the pressurizing chamber 326a) A communication pipe 931 that communicates with a space between the bottom surface and a pressure regulator (decompressor) 932 provided in the middle of the communication pipe 931 is provided.

By providing such a pressurized fluid supply unit 930, a low-temperature fluid of, for example, 15 MPa reduced in pressure by the pressure regulator 932 can be supplied to the inside of the cylinder 326, so that one end surface of the piston head 325 (compression The difference between the pressure on the surface) side and the pressure on the other end surface side can be reduced, and a bellows with low pressure resistance can be used.
Other functions and effects are the same as the functions and effects of the thirteenth embodiment described above, and a description thereof is omitted here.
In addition, the code | symbol 912 in a figure has shown the pump part.

The present invention is not limited to the above-described embodiment. For example, as the bellows 336, 337, 737, 837, one having a cross section shown by a solid line or a two-dot chain line in FIG. it can.
That is, a convex shape having one bulge on the radially outer side indicated by a solid line in FIG. 22 or a concave shape having a single dent on the radial inner side indicated by a two-dot chain line in FIG. It can also be.

Moreover, the heat insulation connection parts 128 and 328 are not limited to what was mentioned above, For example, it can also be set as shown in FIG.
23 is insulated between the tip 428a of the rod 320 formed in a T shape in cross section and the other end 428b of the piston rod 322 also formed in a T shape in cross section. The material 428c is interposed, and these members are connected by fastening members J such as bolts and nuts, for example.

  Furthermore, in the embodiment described with reference to FIG. 17, the two-stage compression using the outer peripheral edge side and the inner peripheral edge side of the piston head 525 has been described, but the present invention is not limited to this, and the piston It is also possible to employ a configuration in which one end surface of the head is further finely divided into concentric circles and can be compressed more than three stages of compression.

  Furthermore, the above-described chamber C and low-pressure chamber 534 are provided with relief valves, and the low-temperature fluid ejected from the relief valves is provided with a pump suction side (or a separate fuel cell) via a return pipe. More preferably, the item is returned to the fuel cell).

A fifteenth embodiment of a booster pump for low temperature fluid according to the present invention will be described with reference to FIG.
As shown in FIG. 24, a cryogenic fluid booster pump 1008 according to the present embodiment is configured with a drive unit 1111 and a pump unit 1112 driven by the drive unit 1111 as main elements.
The drive unit 1111 includes a rod 1115 and a power transmission unit 1116 that transmits power from a drive source (not shown) (for example, an electric motor or an engine) to the rod 1115.
The rod 1115 is a substantially rod-like member that extends downward from the lower end surface of the power transmission unit 1116 and has a circular shape in cross section, and a heat insulating connection portion 328 is provided at the lower end portion thereof.
The power transmission unit 1116 linearly reciprocates the rod 1115 in the vertical direction (in the direction of the arrow in FIG. 24) with a stroke of 2 mm, for example, by power from a drive source (not shown).

The pump unit 1112 includes a piston 1121, a piston rod 1122, and a cylinder block 1123.
The piston 1121 includes one connecting member 1124 and one or a plurality (four in this embodiment) of piston heads 1125, and can reciprocate in a cylinder 1126 formed inside the cylinder block 1123. Contained.
The connecting member 1124 is a member having a substantially disk shape. One end of the piston rod 1122 is connected to the center of the connecting member 1124, and the lower end surface of each piston head 1125 is connected to the outer periphery of the connecting member 1124. Four rods 1127 are provided to connect the end faces. As shown in FIG. 25, these four rods 1127 are arranged at equal intervals (intervals of 90 °).
Each piston head 1125 is a member having a substantially disk shape, and a low-temperature fluid (for example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide, liquefied natural gas, etc.), liquefied by one end face (the upper end face in FIG. 24). Propane gas or the like can be compressed.

The piston rod 1122 is a substantially rod-like member having a circular shape in cross section, and has one end connected to the upper end surface of the connecting member 1124 and the other end connected to the heat insulating connecting portion 328 as described above. To the tip of the rod 1115 (the lower end in FIG. 24).
The heat insulation connecting portion 328 includes a tip portion 328a of a rod 1115 having the same form as the inner race of the rolling bearing, a second end portion 328b of a piston rod 1122 having the same form as the outer race of the rolling bearing, and the rod 1115. A plurality of (four in this embodiment) rolling elements (for example, balls and rollers) 328c disposed between the tip 328a and the other end 328b of the piston rod 1122 are provided.
As a result, the tip end portion 328a of the rod 1115 and the other end portion 328b of the piston rod 1122 are connected by point contact or line contact via the rolling element 328c, so that the rod 1115 is moved to the piston rod 1122. The heat transfer (heat input) is greatly cut off.
Also, since the piston rod 1122 is designed to be as long as possible, even if there is heat transfer (heat input) from the rod 1115 to the piston rod 1122, the piston rod 1122 Heat transmission (heat input) to the connecting member 1124 is minimized.

A through hole 323a through which the rod 1115 penetrates is formed at the center of the top of the cylinder block 1123, and the inside of the top of the cylinder block 1123 communicates with the through hole 323a and accommodates the heat insulating connecting portion 328. A space 329 is formed.
Further, inside the cylinder block 1123 positioned below the internal space 329, a cylinder 1126 communicating with the internal space 329 through a through hole 1123b through which the piston rod 1122 passes is provided in the longitudinal direction (vertical direction in FIG. 24). Is drilled along. One end side (the upper side in FIG. 24) of the cylinder 1126 is a pressurizing chamber 1126a having an inner diameter larger than the outer diameter of the piston head 1125, and the piston head 1125 can be accommodated in the pressurizing chamber 1126a. ing.
As indicated by reference numeral 1123c, the inside of the side wall, the inside of the bottom surface, and the inside of the top surface of the cylinder block 1123 have a heat insulating vacuum structure that is hollow and evacuated.

On the other hand, in the cylinder block 1123 positioned between the pressurizing chamber 1126a and the internal space 329 and at positions opposed to the central portion on the one end surface side of the piston head 1125, suction is connected to each pressurizing chamber 1126a. A port 1123d and a discharge port 1123e are provided. Each of the suction port 1123d and the discharge port 1123e is provided with a ball type check valve 1130 so as to control the suction and discharge of the low temperature fluid.
Each suction port 1123d is provided in communication with a fluid suction path 1131 drilled in the cylinder block 1123, while each discharge port 1123e is provided in communication with a fluid discharge path 1132 drilled in the cylinder block 1123. It has been. Accordingly, the low-temperature fluid introduced into the pressurizing chamber 1126a from the fluid suction path 1131 through the suction port 1123d is compressed by one end surface of the piston head 1125, and is pressurized (pressurized) to 30 MPa, for example, and then discharged. The port 1123e is led out of the cylinder block 1123 through the fluid discharge path 1132.
The low-temperature fluid led out of the cylinder block 1123 through the fluid discharge path 1132 is temporarily stored (stored) in the chamber 1134 via the pipe 1133. The low-temperature fluid stored in the chamber 1134 is led to the heat exchanger 1136 through the pipe 1135 and gasified, and most of the low-temperature fluid is supplied to the fuel injection device (not shown) through the pipe 1137. And a part thereof is connected to the inside of the cylinder 1126 (the other end side of the cylinder 1126, that is, on the side opposite to the pressurizing chamber 1126a) via the pipe 1138 and the pressure regulator (decompressor) 1139. To the bottom surface of the cylinder 1126).
In the chamber 1134, for example, a low-temperature fluid whose pressure has been increased to 30 MPa is stored.
Further, the cylinder 1126 is supplied with a gasified low-temperature fluid of, for example, 15 MPa that has been decompressed by the pressure regulator 1139.

A bellows (partition member) 1140 is provided in each pressurizing chamber 1126a. The bellows 1140 includes an inner peripheral side (rod 1127 side) and an outer peripheral side (cylinder block 1123 side) of the pressurizing chamber 1126a located on the connecting member 1124 side (lower side in FIG. 24) from the piston head 1125. One end of the piston head 1125 is attached to the surface opposite to the one end surface (the other end surface), and the other end is attached to the inner wall surface of the cylinder block 1123.
A bellows (partition member) 1141 is also provided on the radially outer side of one end of the piston rod 1122. The bellows 1141 partitions (separates) at one end of the piston rod 1122 into an inner peripheral side (piston rod 1122 side) and an outer peripheral side (cylinder block 1123 side), and one end thereof is a connecting member. The other end is attached to the inner wall surface of the cylinder block 1123 while being attached to the upper end surface of 1124.
Each of these bellows 1140 and 1141 is made of, for example, stainless steel or Inconel, which has elasticity at a (very) low temperature.
In addition, the code | symbol 1142, 1143, and 1144 in FIG. 24 are each a cyclic | annular (for heat insulation) sealing member by planar view.
FIG. 25 is a sectional view taken along arrow XXV-XXV in FIG.

  From the above configuration, when the rod 1115 of the drive unit 1111 linearly reciprocates in the vertical direction, the piston rod 1122 coupled to the rod 1115 via the heat insulating connection unit 328 linearly reciprocates in the vertical direction together with the piston 1121. The low-temperature fluid sucked from the suction port 1123d is compressed by the one end surface of the piston head 1125 and pressurized (pressure-increasing), and then passes from the discharge port 1123e to the outside of the cylinder block 1123 through the fluid discharge path 1132. It has been derived.

According to the booster pump 1008 for low-temperature fluid according to the present embodiment, the low-temperature fluid is compressed by one end surface of the piston head 1125 by pulling the piston rod 1122 toward the drive unit 1111 (upward in FIG. 24). It has become. That is, the compression force is not applied to the piston rod 1122 when the low temperature fluid is compressed.
As a result, the diameter of the piston rod 1122 can be made smaller than that of the conventional piston rod in which the compression force is applied to the piston rod, so that heat input from the drive source can be reduced and the weight of the piston rod 1122 can be reduced. Can be achieved, and the overall weight of the pump can be reduced.

Further, since there is no portion that moves in contact with the inner peripheral surface of the pressurizing chamber 1126a (for example, a conventional piston ring), heat generation in the pressurizing chamber 1126a can be prevented, and a low-temperature fluid can be supplied. Heating can be prevented.
Furthermore, since the inner peripheral side (radially inner side) and the outer peripheral side (radially outer side) of the pressurizing chamber 1126a are completely separated by the bellows 1140, the pressurizing chamber is separated from the inner peripheral side of the pressurizing chamber 1126a. It is possible to prevent leakage of the low temperature fluid from the outer peripheral side of 1126a (or from the outer peripheral side of the pressurizing chamber 1126a to the inner peripheral side of the pressurizing chamber 1126a). Can be improved.
Furthermore, outside the bellows 1140 (outside in the radial direction), there is a low-temperature fluid that is gasified by the heat exchanger 1136 and whose pressure is adjusted to a predetermined pressure (for example, 15 MPa) by the pressure regulator 1139. Therefore, the deformation of the bellows 1140 when compressing the low-temperature fluid sucked into the bellows 1140 can be reduced, the life of the bellows 1140 can be extended, and the booster pump 1008 for low-temperature fluid. Reliability can be improved.

Furthermore, the heat input from the rod 1115 to the piston rod 1122 can be reduced by the heat insulating connecting portion 328, and the heat input from the drive source can be further reduced.
Furthermore, a connecting member 1124 is provided between the piston rod 1122 and the piston head 1125, and heat from the piston rod 1122 reaches the piston head 1125 after passing through the connecting member 1124. The amount of heat can be further reduced.
Furthermore, since the rod 1115 connected to the power transmission unit 1116 extends on the same side as the side where the suction port 1123d and the discharge port 1123e are arranged (upper side in FIG. 24), the longitudinal direction (axial direction) of the pump unit 1112 ) Can be shortened, and the length of the entire pump in the longitudinal direction (axial direction) can be shortened, so that the pump can be reduced in size and weight.

A sixteenth embodiment of a cryogenic fluid booster pump according to the present invention will be described with reference to FIG.
The cryogenic fluid booster pump 2009 according to the present embodiment is a so-called swash plate type (or swash type), and is composed mainly of a drive unit 2161 and a pump unit 2162 driven by the drive unit 2161. Is.
In addition, the same code | symbol is attached | subjected to the component same as 15th Embodiment mentioned above.

The drive unit 2161 includes a rod 2165 and a power transmission unit 2166 that transmits power from a drive source (not shown) (for example, an electric motor or an engine) to the rod 2165.
The rod 2165 is a substantially rod-shaped member that extends downward from the lower end surface of the power transmission unit 2166 and has a circular shape in cross section.
The power transmission unit 2166 rotates the rod 2165 in one direction (in the direction of the arrow in FIG. 26) with power from a drive source (not shown).

The pump portion 2162 includes one or a plurality (four in this embodiment) of pistons 2171, a swash plate (also referred to as “yoke”) 2172, and a cylinder block 2173.
Each piston 2171 has a piston head 2171a at one end and a piston shoe 2171b at the other end, and is a substantially rod-like member having a circular shape in cross section, and is housed in a cylinder 2176 so as to be able to reciprocate. .
The piston head 2171a is a so-called enlarged portion having an outer diameter larger than the outer diameter of the piston rod 2171c connecting the piston head 2171a and the piston shoe 2171b, and has a flat one end face (FIG. 26). (For example, liquid hydrogen, liquid nitrogen, liquefied carbon dioxide gas, liquefied natural gas) in order to compress liquefied propane gas or the like.
Like the piston head 2171a, the piston shoe 2171b has a larger outer diameter than the piston rod 2171c, and is a so-called enlarged portion, and its end surface (the lower surface in FIG. 26) It is configured to slide along the sliding surface P of the swash plate 2172 having an inclination angle.

The cylinder block 2173 has pressurizing chambers 1126a drilled along the longitudinal direction (vertical direction in FIG. 26) by the same number as the number of pistons 2171 therein, and in each pressurizing chamber 1126a. Each includes one piston head 2171a.
As shown in FIG. 26, a piston shoe 2171b and a swash plate 2172 are accommodated on the other end side (lower side in FIG. 26) of the cylinder 2176.
A through hole 1123a through which the rod 2165 passes is formed at the center of the cylinder block 2173, and the inside of the side wall, the inside of the bottom surface, and the inside of the top surface of the cylinder block 2173 are hollow as shown by reference numeral 1123c. A heat-insulating vacuum structure that is evacuated with

On the other hand, a suction port 1123d and a discharge port 1123e communicating with each pressurizing chamber 1126a are provided in the top portion of the cylinder block 2173 and at positions facing the central portion on the one end surface side of the piston head 2171a. Each of the suction port 1123d and the discharge port 1123e is provided with a ball type check valve 1130 so as to control the suction and discharge of the low temperature fluid.
Each suction port 1123d is provided in communication with a fluid suction path 1131 drilled in the cylinder block 2173, while each discharge port 1123e is provided in communication with a fluid discharge path 1132 drilled in the cylinder block 2173. It has been. Therefore, the low-temperature fluid introduced into the pressurizing chamber 1126a from the fluid suction path 1131 through the suction port 1123d is compressed by one end face of the piston head 2171a and, for example, pressurized (pressurized) to 30 MPa and then discharged. It is led out of the cylinder block 2173 through the fluid discharge path 1132 from the port 1123e.
The low-temperature fluid guided to the outside of the cylinder block 2173 through the fluid discharge path 1132 is temporarily stored (stored) in the chamber 1134 via the pipe 1133. The low-temperature fluid stored in the chamber 1134 is led to the heat exchanger 1136 through the pipe 1135 and gasified, and most of the low-temperature fluid is supplied to the fuel injection device (not shown) through the pipe 1137. And a part of the inside of the pressurizing chamber 1126a via the pipe 1138 and the pressure regulator (decompressor) 1139 (that is, the space on the other end surface side of the piston head 2171a located on the side opposite to the bellows 1140). To be guided to.
In the chamber 1134, for example, a low-temperature fluid whose pressure has been increased to 30 MPa is stored.
The pressurized chamber 1126a is supplied with a gasified low-temperature fluid of, for example, 15 MPa that has been decompressed by the pressure regulator 1139.

A bellows (partition member) 1140 is provided in each pressurizing chamber 1126a. The bellows 1140 includes an inner peripheral side (piston rod 2171c side) and an outer peripheral side (cylinder block 2173 side) of the pressurizing chamber 1126a located on the piston shoe 2171b side (lower side in FIG. 26) than the piston head 2171a. And one end of the piston head 2171a is attached to the surface opposite to the one end surface (the other end surface), and the other end is attached to the inner wall surface of the cylinder block 2173. .
A bellows (partition member) 2180 is also provided on the radially outer side of one end of the piston rod 2171c. The bellows 2180 partitions (separates) the piston rod 2171c into an inner peripheral side (piston rod 2171c side) and an outer peripheral side (cylinder block 2173 side) at one end portion of the piston rod 2171c. The other end of 2171b (the upper surface in FIG. 26) is attached to the outer peripheral end, and the other end is attached to the inner wall surface of cylinder block 2173.
Each of these bellows 1140 and 2180 is made of, for example, stainless steel or Inconel having elasticity at (very) low temperatures.
In FIG. 26, reference numerals 1142, 1143, and 1144 are respectively annular (thermal insulating) seal members in plan view, and reference numerals 2181 and 2182 are thrust roller bearings.

  From the above configuration, when the rod 2165 is rotated (in one direction) by the drive source, the piston shoe 2171b slides along the sliding surface P via the thrust bearing 2181 and the piston 2171 is moved in the cylinder 2176. The low-temperature fluid that has been reciprocated and has flowed into the pressurizing chamber 1126a is successively compressed. In the present embodiment, the stroke of the piston 2171 is set to 2 mm, for example.

According to the cryogenic fluid booster pump 2009 according to the present embodiment, the rod 2165 is rotated in one direction (the direction of the arrow in FIG. 26), whereby the cryogenic fluid is compressed by one end face of the piston head 2171a. ing. That is, the compression force is not applied to the rod 2165 when compressing the low temperature fluid.
Thereby, since the diameter of the rod 2165 can be made smaller than that of the conventional piston rod type in which compression force is applied to the rod, heat input from the drive source can be reduced, and the weight of the rod 2165 can be reduced. Can be achieved, and the overall weight of the pump can be reduced.

Further, since there is no portion that moves in contact with the inner peripheral surface of the pressurizing chamber 1126a (for example, a conventional piston ring), heat generation in the pressurizing chamber 1126a can be prevented, and a low-temperature fluid can be supplied. Heating can be prevented.
Further, since the inner peripheral side (radially inner side) and the outer peripheral side (radial outer side) of the pressurizing chamber 1126a are completely separated by the bellows 1140, the pressurizing chamber is separated from the inner peripheral side of the pressurizing chamber 1126a. It is possible to prevent leakage of the low temperature fluid from the outer peripheral side of 1126a (or from the outer peripheral side of the pressurizing chamber 1126a to the inner peripheral side of the pressurizing chamber 1126a), and to improve the compression efficiency of the booster pump 2009 for the low temperature fluid. Can be improved.
Furthermore, outside the bellows 1140 (outside in the radial direction), there is a low-temperature fluid that is gasified by the heat exchanger 1136 and whose pressure is adjusted to a predetermined pressure (for example, 15 MPa) by the pressure regulator 1139. Therefore, the deformation of the bellows 1140 when compressing the low temperature fluid sucked into the bellows 1140 can be reduced, the life of the bellows 1140 can be extended, and the booster pump 2009 for low temperature fluid Reliability can be improved.

Furthermore, since the rod 2165 connected to the power transmission unit 2166 extends on the same side as the side where the suction port 1123d and the discharge port 1123e are arranged (upper side in FIG. 26), the longitudinal direction (axial direction) of the pump unit 2162 ) Can be shortened, and the length of the entire pump in the longitudinal direction (axial direction) can be shortened, so that the pump can be reduced in size and weight.

  In the above-described embodiment, a four-cylinder type having four pistons and four cylinders has been described. However, the present invention is not limited to this, and for example, a single cylinder, a two-cylinder, or a three-cylinder Alternatively, a configuration with five or more cylinders may be employed.

Further, the thrust roller bearing 2182 described in the sixteenth embodiment is not limited to one supporting the central portion of the lower surface of the swash plate 2172 as shown in FIG. It can also be supported by a plurality of thrust roller bearings arranged in the direction.
Furthermore, it is preferable that the angle of the swash plate 2172 is configured to be changeable by using an actuator or the like, that is, configured to be a variable capacity type. As a result, the pump discharge amount can be changed only by changing the angle of the swash plate 2172 without changing the drive rotational speed of the pump.

  Furthermore, in the above-described embodiment, the ball-type check valve 1130 is provided for each of the suction port 1123d and the discharge port 1123e, but the present invention is not limited to this, and can be found in a DOHC such as an internal combustion engine. Such a forced drive type may be used, or a configuration such as a reed valve, a poppet valve, or the like may be employed.

Furthermore, the present invention is not limited to the above-described embodiment. For example, as the bellows 1140, 1141, 2180, one having a cross section as shown by a solid line or a two-dot chain line in FIG. You can also.
That is, a convex shape having one bulge on the radially outer side indicated by a solid line in FIG. 22 or a concave shape having a single dent on the radial inner side indicated by a two-dot chain line in FIG. It can also be.

  Furthermore, the heat insulation connection part 328 shown in FIG. 24 is not limited to what was mentioned above, For example, it can also be as shown in FIG.

  Furthermore, the above-described chamber 1134 is provided with a relief valve, and the low-temperature fluid ejected from the relief valve is supplied via the return pipe to the pump suction side (or a fuel cell provided with a separate fuel cell). It is more preferable that the battery is returned to the battery.

  Furthermore, the drive unit 311 in the eighth to fourteenth embodiments is not limited to the cam drive shown in the figure, and forcibly drives the rod 320, such as a crank drive. It can also be.

  Furthermore, in the fifteenth and sixteenth embodiments, the piston rod 1122 and the connecting member 1124 are the rod 2165 and the swash plate 2172, respectively, and the heat insulating material 327 described in the eighth to fourteenth embodiments. It is more preferable that they are connected (connected) via.

Furthermore, in each of the above-described eighth to fifteenth embodiments, a piston body, a piston head, and the like that are housed in a cylinder and reciprocate in the cylinder are attached to the inner wall surface (cylinder wall) of the cylinder. For example, a guide member is provided between the piston rods 322 and 1122 and the cylinder blocks 323 and 1123, between the piston main bodies 324 and 524 and the cylinder 326, or between the connecting member 1124 and the cylinder 1126 so as not to collide. It is more preferable that it is used.
As the guide member, for example, between the piston rods 322 and 1122 and the cylinder blocks 323 and 1123, between the outer peripheral surface of the piston main bodies 324 and 524 and the inner wall surface of the cylinder 326, or the outer peripheral surface of the connecting member 1124 and the cylinder A linear bearing disposed between the inner wall surface of 1126 and a cylindrical protrusion protruding downward from the lower end surfaces of the piston bodies 324 and 524 are formed in a cylindrical recess formed at the center of the bottom surface of the cylinders 326 and 1126. The thing guided to the place (dent) can be mentioned.
As a result, the reciprocating members such as the piston main body and the piston head reciprocate without shaking or vibrating in the cylinder, and the reciprocating member can be prevented from colliding with the inner wall surface of the cylinder. In addition, the reciprocating member can be smoothly driven with minimal power.

Furthermore, in each of the above-described fourteenth to sixteenth embodiments, the space in which the low-temperature fluid gasified in these embodiments is supplied can be in a vacuum state.
Thereby, while the temperature rise of a cylinder block is suppressed, the temperature rise of the low-temperature fluid which flows in into a pressurization chamber will be suppressed.
At this time, the pipes 931 and 1138 and the pressure regulator 1139 shown in FIGS. 21, 24 and 26 are omitted.

Furthermore, in the above-described embodiment, it is more preferable that a space is formed between the piston rods 322 and 1122 and the cylinder blocks 323 and 1123 in a vacuum state.
For example, in the fifteenth embodiment shown in FIG. 24, a space on the inner peripheral side and a space on the outer peripheral side of the piston rod 1122 are provided between the lower surface of the other end 328b of the piston rod 1122 and the upper surface of the bottom of the internal space 329. A separate bellows (similar to bellows 1141) is provided.
That is, the space between the cylinder block 1123 and the piston rod 1122 is in a vacuum state, and heat from the piston rod 1122 (that is, heat that has entered the piston rod 1122 side from the drive source 1111 side) to the cylinder block 1123. ) Is prevented from being transmitted.
Thereby, the temperature rise of the cylinder block 1123 is suppressed, and the temperature rise of the low-temperature fluid flowing into the pressurizing chamber 1126a is suppressed.

As used herein, “low temperature” refers to about −273 ° C. to 0 ° C. or less, and “high pressure” refers to 0.2 MPa to 200 MPa.
In addition, “fluid” in the present specification includes “liquid”, “gas”, and “colloid”.

Claims (35)

A piston having a piston head and a piston rod;
A pressurizing pump comprising: a cylinder that houses the piston head and has a pressurizing chamber in which fluid is compressed by one end surface of the piston head;
A booster pump characterized in that the piston head is provided with a bellows for separating a space on the piston rod side and a space on the cylinder side of the pressurizing chamber.   2. The booster pump according to claim 1, wherein a filler filling a space existing between an outer surface of the bellows and an inner peripheral surface of the cylinder is disposed.   The booster pump according to claim 1 or 2, wherein a ring-shaped seal member is disposed at one end of the bellows on the piston head side.   The booster pump according to any one of claims 1 to 3, wherein the piston rod has a heat-insulating vacuum structure that is hollow and evacuated. A booster device comprising at least two booster pumps according to any one of claims 1 to 4,
A booster characterized in that multistage compression is performed by these booster pumps. A cryogenic fluid storage tank for storing cryogenic fluid at a low temperature,
A booster pump according to any one of claims 1 to 4, or a booster device according to claim 5,
A cryogenic fluid storage tank in which cryogenic fluid is stored;
A cryogenic fluid storage tank, comprising: the boosting pump or the boosting device; and a cryogenic container in which the cryogenic fluid storage tank is accommodated.   The cryogenic fluid storage tank according to claim 6, wherein the booster pump or the booster device is disposed downstream of the cryogenic fluid storage tank and outside the cryogenic fluid storage tank.   The cryogenic fluid storage tank according to claim 6 or 7, wherein a cryogenic slush fluid in a solid-liquid two-phase state is stored in the cryogenic fluid storage tank.   The storage tank for cryogenic fluid according to claim 8, wherein a mesh is disposed at an outlet of the cryogenic fluid storage tank.   The storage tank for cryogenic fluid according to claim 9, wherein a heater is disposed in the cryogenic fluid storage tank.   The storage tank for cryogenic fluid according to any one of claims 6 to 10, wherein a heat exchanger is disposed downstream of the booster pump or the booster.   The storage tank for cryogenic fluid according to any one of claims 6 to 11, wherein a radiation shield plate is provided on an inner surface of the cryogenic container. A low temperature in which a low-temperature fluid is compressed by one end face of the piston head, and includes a cylinder block having a pressurizing chamber therein and a piston head which is housed in the pressurizing chamber and reciprocates in the pressurizing chamber. A fluid booster pump,
Separating the inner circumferential side space and the outer circumferential side space of the piston head between one end surface of the piston head and the inner surface of the pressurizing chamber facing the one end surface. A pressurizing pump for low-temperature fluid, characterized in that a partition member is provided.   The pressurized pump for cryogenic fluid according to claim 13, wherein a pressurized fluid is filled outside the partition member.   The booster pump for low-temperature fluid according to claim 13, wherein the outside of the partition member is in a vacuum state. A piston rod driven by a drive connected to a drive source;
A piston head connected to the piston rod and reciprocating with the piston rod;
A cryogenic fluid booster pump comprising: a cylinder that houses the piston head and has a pressurized chamber in which a cryogenic fluid is compressed by one end surface of the piston head;
The drive unit is disposed on one end surface side of the piston head, and when compressing a low-temperature fluid, a tensile force in a direction substantially the same as the extending direction of the shaft portion is applied to the shaft portion of the piston rod. A booster pump for low temperature fluids.   The piston head is divided into at least two members having concentric circles, and the cryogenic fluid is gradually increased to a desired pressure by sequentially passing through one end faces of the divided piston heads. The pressurizing pump for low-temperature fluid according to claim 16, wherein the pump is a multistage compression structure.   A flexible partition member that separates a piston rod side space and a cylinder side space of the pressurizing chamber is provided on one end surface side and the other end surface side of the piston head, respectively. The pressurizing pump for low-temperature fluid according to claim 16 or 17.   The flexible partition member for separating the space on the piston rod side and the space on the cylinder side of the pressurizing chamber is provided on the other end surface side of the piston head. A pressurizing pump for low-temperature fluid as described in Item 17.   The precooling layer is formed in the inside of the cylinder, The pressurizing pump for low-temperature fluid according to any one of claims 16 to 19 characterized by things.   21. The cryogenic fluid booster pump according to any one of claims 16 to 20, wherein the drive unit and the piston rod are connected to each other through a heat insulating connection unit.   The booster pump for low-temperature fluid according to any one of claims 16 to 21, wherein the piston head and the piston rod are connected via a heat insulating material.   23. The booster for low-temperature fluid according to claim 16, wherein a guide member for guiding a shaft portion of the piston rod is provided between the cylinder block and the piston rod. pump.   24. The booster pump for cryogenic fluid according to claim 16, wherein a space between the cylinder block and the shaft portion of the piston rod is configured to be in a vacuum state. .   The said cylinder is comprised so that attachment or detachment with respect to the said cryogenic fluid storage tank is carried out while being immersed in the cryogenic fluid stored in the inside of the cryogenic fluid storage tank. A booster pump for cryogenic fluid according to claim 1.   The drive unit and the cylinder are soaked in a cryogenic fluid stored in a cryogenic fluid storage tank, and are configured to be detachable from the cryogenic fluid storage tank. 25. The pressurizing pump for low-temperature fluid according to any one of items 1 to 24. A booster pump for cryogenic fluid according to any one of claims 16 to 26;
A chamber for storing a cryogenic fluid boosted by the cryogenic fluid booster pump;
And a fuel injection device to which a low-temperature fluid is supplied from the chamber.   A pressurizing fluid supply unit is provided in which the cryogenic fluid in the chamber is liquefied or gasified and supplied into the cylinder located on the other end face side of the piston head of the cryogenic fluid booster pump. The cryogenic fluid supply apparatus according to claim 27.   A heat exchanger for gasifying liquid hydrogen is provided between the chamber and the fuel injection device, the pressure of the gasified hydrogen is adjusted, and the heat exchanger is positioned on the other end face side of the piston head of the booster pump for low-temperature fluid. 28. The cryogenic fluid supply apparatus according to claim 27, further comprising: a pressurized fluid supply unit that supplies the pressurized fluid into the cylinder.   30. The cryogenic fluid supply apparatus according to any one of claims 27 to 29, wherein a relief valve is provided in the chamber. A low temperature in which a low-temperature fluid is compressed by one end face of the piston head, and includes a cylinder block having a pressurizing chamber therein and a piston head which is housed in the pressurizing chamber and reciprocates in the pressurizing chamber. A fluid booster pump,
A cryogenic fluid pressure booster characterized in that a flexible partition member is provided on the other end surface side of the piston head to separate a space on the inner peripheral side and a space on the outer peripheral side of the pressurizing chamber. pump.   32. The booster pump for low temperature fluid according to claim 31, wherein the inside of the partition member is filled with a pressurized fluid.   32. The booster pump for low temperature fluid according to claim 31, wherein the inside of the partition member is in a vacuum state.   34. The cryogenic fluid use according to any one of claims 16 to 26 and 31 to 33, wherein a guide member for guiding the piston head is provided between the cylinder block and the piston head. Booster pump. 16. The cylinder block according to claim 13, wherein the cylinder block is immersed in a cryogenic fluid stored in a cryogenic fluid storage tank and is detachable from the cryogenic fluid storage tank. The booster pump for low-temperature fluid according to any one of 31 to 34.

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