WO2018181975A1

WO2018181975A1 - Reciprocating booster compressor

Info

Publication number: WO2018181975A1
Application number: PCT/JP2018/013815
Authority: WO
Inventors: 井上　弘
Original assignee: アネスト岩田株式会社
Priority date: 2017-03-31
Filing date: 2018-03-30
Publication date: 2018-10-04
Also published as: CN110431306A; EP3604807A1; EP3604807A4; JPWO2018181975A1

Abstract

In this reciprocating booster compressor, the interior of a crank case, which accommodates a crank mechanism, is divided by a dividing wall into a first space and a second space. At least one of the first space and the second space is pressurized by the introduction of a gas pressurized in a first cylinder or a second cylinder, and is thereby set to a pressure corresponding to the first cylinder and the second cylinder.

Description

Reciprocating booster compressor

This disclosure relates to a reciprocating booster compressor capable of further compressing pressurized gas supplied from the outside by reciprocating movement of a piston in a cylinder.

Generally, in a reciprocating compressor, the rotational movement of an input shaft to which power is input from a power source such as an electric motor is converted into the reciprocating movement of a piston in a cylinder by a crank mechanism housed in the crankcase. Thereby, compression of the gas supplied from the outside is performed. In recent years, in this type of compressor, in addition to the increasing demand for compressed gas at a higher pressure, there is a so-called booster compressor for further boosting a gas that has been previously pressurized to atmospheric pressure or higher from the viewpoint of energy saving. Are known.

In reciprocating booster compressors, gas above atmospheric pressure is targeted for compression. Therefore, if the inside of the crankcase is at atmospheric pressure, the pressure difference between the compression chamber defined by the cylinder and the piston and the crankcase increases, and a large load is applied to components such as the crankshaft bearing member constituting the crank mechanism. Take it. As a result, the product life is shortened. Further, if the crankcase is at atmospheric pressure, it is difficult to obtain an energy saving effect. Therefore, this type of reciprocating booster compressor pressurizes the inside of the crankcase and reduces the pressure difference with the compression chamber, thereby suppressing the load during the suction stroke and obtaining a high energy saving effect. For example, in Patent Document 1, the pressure difference between the compression chamber and the crankcase is reduced by accumulating the pressurized gas formed in the compression chamber in a tank and supplying a part thereof into the crankcase.

JP 2009-133282 A

In this type of compressor, a multistage reciprocating booster compressor is required to meet the demand for pressurized gas at higher pressure. For example, in the case of a two-stage system in which a first cylinder having a low pressure side compression chamber and a second cylinder having a high pressure side compression chamber are connected in series, the pressurized gas supplied from the outside is the first After being compressed in the cylinder, it is further compressed in the second cylinder. The first cylinder and the second cylinder that perform such compression may be driven by a common crank mechanism. However, since the first cylinder and the second cylinder handle pressurized gases having different pressures, if the pressure of the crankcase is increased to an appropriate pressure for one cylinder, the pressure of the crankcase Is not an appropriate pressure for the other cylinder, and the pressure difference between the crankcase and the other cylinder is inappropriate. Therefore, if the configuration in the single cylinder as in Patent Document 1 is applied as it is to the configuration having a plurality of cylinders, it is inevitable that such an inappropriate pressure difference occurs. As a result, the load on the drive shaft and the like is increased, and it is difficult to obtain a high energy saving effect.

Note that such a large load is a factor that shortens the product life as described above. In order to prevent the product life from being shortened, for example, it is conceivable to make a heavy-duty design capable of withstanding a pressure difference.

At least one embodiment of the present invention has been made in view of the above circumstances, and in each cylinder that performs multi-stage compression, by appropriately setting the internal pressure of the crankcase, it is possible to achieve a long life and achieve high energy savings. An object of the present invention is to provide a reciprocating booster compressor capable of obtaining an effect.

(1) In order to solve the above problems, a reciprocating booster compressor according to at least one embodiment of the present invention includes a crank mechanism for converting rotational motion of an input shaft to which power is input into reciprocating motion, And a plurality of cylinders capable of compressing gas by being driven by a reciprocating motion converted by the crank mechanism, wherein the plurality of cylinders are supplied from outside. A first cylinder that generates a first pressurized gas having a pressure higher than that of the pressurized gas by compressing the pressurized gas is connected in series to the first cylinder, and the first pressurized gas is further reduced. And a second cylinder that generates a second pressurized gas having a pressure higher than that of the first pressurized gas by compression, wherein the crankcase has a first space corresponding to the first cylinder. And corresponding to the second cylinder And the first space and the second space are separated from each other by a partition wall provided inside the crankcase, and at least the first space or the second space. One is pressurized by introducing any one of the pressurized gas, the first pressurized gas, or the second pressurized gas.

According to the configuration of (1) above, the crankcase has a first space and a second space corresponding to a plurality of cylinders. Since the first space and the second space are separated from each other by the partition wall, the first space and the second space can form independent pressures. At least one of the first space and the second space is pressurized by introducing any one of a pressurized gas, a first pressurized gas, and a second pressurized gas, whereby each cylinder The pressure difference from the crankcase side can be suppressed.

(2) In some embodiments, in the configuration of (1), the pressurized gas is introduced into the first space, and the first pressurized gas is introduced into the second space. Is done.

According to the configuration of (2) above, the pressure corresponding to the intake pressure of the first cylinder is set by introducing the pressurized gas supplied to the first cylinder into the first space. On the other hand, by introducing the first pressurized gas supplied to the second cylinder into the second space, the pressure is set to be different from that of the first space corresponding to the intake pressure of the second cylinder. The

(3) In some embodiments, in the configuration of (2) above, the first passage connecting the intake port of the pressurized gas and the first space, the first space, and the first space And a second passage connecting the suction side of the cylinder.

According to the configuration of (3) above, the pressurized gas that is the compression target of the booster compressor is supplied to the first space via the first passage. The pressurized gas supplied to the first space passes through the first space and is supplied to the first cylinder via the second passage. As described above, since the pressurized gas is supplied to the first cylinder via the first space, the pressure corresponding to the first cylinder is effective in the first space by the dynamic pressure of the pressurized gas. Can be formed.

(4) In some embodiments, in the above configuration (2) or (3), a third passage connecting the discharge side of the first cylinder and the second space, and the second space And a fourth passage connecting the suction side of the second cylinder.

According to the configuration of (4) above, the first pressurized gas discharged from the first cylinder is supplied to the second space via the third passage. The pressurized gas supplied to the second space passes through the second space and is supplied to the second cylinder via the fourth passage. Thus, since the 1st pressurized gas is supplied to the 2nd cylinder via the 2nd space, in the 2nd space, it corresponds to the 2nd cylinder with the dynamic pressure which pressurized gas has. Pressure can be formed effectively.

(5) In some embodiments, in the configuration of (4) above, a heat radiating fin is provided on the outer surface of the third passage.

Since the first pressurized gas is heated by being compressed in the first cylinder, it is preferably cooled before being supplied to the second cylinder. According to the configuration of (5) above, since the radiation fins are provided on the outer surface of the third passage through which the first pressurized gas discharged from the first cylinder passes, the first pressurized gas The cooling is promoted by the radiation fins when passing through the third passage. Thereby, the intermediate cooler provided between the first cylinder and the second cylinder can be reduced in size, or if the cooling effect by the radiation fins is sufficient, it is not necessary to provide the intermediate cooler. The apparatus can be reduced in size.

(6) In some embodiments, in the above configuration (2) or (3), a fifth passage connecting the discharge side of the first cylinder and the suction side of the second cylinder; And a sixth passage branched from the fifth passage and connected to the second space.

According to the configuration of (6) above, the first pressurized gas discharged from the first cylinder is supplied to the second cylinder via the fifth passage. Here, the fifth passage is provided with a sixth passage that branches into the second space, and a part of the first pressurized gas is supplied to the second space, whereby the second space is provided. Can be pressurized. In this case, since the sixth passage can be designed independently of the fifth passage for supplying the first pressurized gas to the second cylinder, a more flexible device configuration can be obtained.

(7) In some embodiments, in the configuration of (6) above, a heat radiating fin is provided on the outer surface of the sixth passage.

Since the first pressurized gas is heated by being compressed in the first cylinder, it is preferably cooled before being supplied to the second cylinder. According to the configuration of (7) above, since the heat radiation fin is provided on the outer surface of the sixth passage through which a part of the first pressurized gas discharged from the first cylinder passes, the first When the pressurized gas passes through the sixth passage, cooling is promoted by the radiation fins. Thereby, the intermediate cooler provided between the first cylinder and the second cylinder can be reduced in size, or if the cooling effect by the radiation fins is sufficient, it is not necessary to provide the intermediate cooler. The apparatus can be reduced in size.

(8) In some embodiments, in any one of the configurations (1) to (7), the partition wall includes an opening through which the input shaft passes, and the input shaft rotatably supported. And a sealing member that seals the opening.

According to the configuration of (8) above, the input shaft passes through the opening provided in the partition wall, so that power can be input to the first cylinder and the second cylinder separated by the partition wall. On the other hand, in the opening portion, the input shaft is sealed while being rotatably supported by the seal member, so that the independence of the first space and the second space partitioned by the partition wall can be ensured. Thereby, the first space and the second space can be appropriately pressurized to the pressure corresponding to each cylinder.

(9) In some embodiments, in the configuration of the above (8), the first space is configured such that the pressurized air introduced into the first space is injected toward the seal member. Is done.

The seal member that seals the opening provided in the partition wall while rotatably supporting the input shaft is likely to become hot when the input shaft rotates. According to the configuration of (9) above, the pressurized air introduced into the first space is jetted toward the seal member with respect to such a seal member, so that the seal member is pressed together with the pressure in the first space. Can be cooled.

(10) In some embodiments, in the configuration according to (8) or (9), the second space is configured such that the first pressurized air introduced into the second space is directed toward the seal member. Configured to be injected.

The seal member that seals the opening provided in the partition wall while rotatably supporting the input shaft is likely to become hot when the input shaft rotates. According to the configuration of (10), the first space is pressurized by injecting the first pressurized air introduced into the second space toward the seal member. At the same time, the sealing member can be cooled.

(11) In some embodiments, in the configuration of (1), the first pressurized gas is introduced into the first space, and the second pressurized gas is introduced into the second space. Gas is introduced.

According to the configuration of (11) above, the first space is pressurized by introducing the first pressurized gas discharged from the first cylinder, so that the first cylinder and the first The pressure difference between the space and the second space can be suppressed, and the second space is pressurized by introducing the second pressurized gas discharged from the second cylinder, so that the second cylinder And the pressure difference between the second space can be suppressed.

(12) In some embodiments, in the configuration of (1) above, the pressurized gas is introduced into the first space, and the second pressurized gas is introduced into the second space. Is done.

According to the configuration of (12) above, the first space is pressurized by introducing pressurized gas that is intake air into the first cylinder, so that the first cylinder and the first space are And the second space is pressurized by introducing a second pressurized gas discharged from the second cylinder, so that the second cylinder and the second cylinder are pressurized. The pressure difference between the two spaces can be suppressed.

(13) In some embodiments, in the configuration of (1), the second pressurized gas is introduced into the first space and the second space.

According to the configuration of (13) above, the first space and the second space are pressurized by introducing the second pressurized gas discharged from the second cylinder, The pressure difference between the crankcase side can be suppressed.

(14) In some embodiments, in any one of the configurations (1) to (13), the oil-free compressor is used.

According to the configuration of (14) above, in an oil-free booster compressor for which a higher discharge pressure is desired in the future, by appropriately setting the pressure in the crankcase, the load during operation is reduced. This can be mitigated, avoiding excessive design of parts such as bearings and pistons, and providing a long product life.

According to at least one embodiment of the present invention, in each cylinder that performs multi-stage compression, by appropriately setting the internal pressure of the crankcase, a reciprocating booster compression that can avoid excessive design and achieve a long life Can provide a machine.

It is sectional drawing which shows the structure of the reciprocating booster compressor which concerns on 1st Embodiment. It is a modification of FIG. It is sectional drawing which shows the structure of the reciprocating booster compressor which concerns on 2nd Embodiment. It is sectional drawing which shows the structure of the reciprocating type booster compressor which concerns on 3rd Embodiment. It is sectional drawing which shows the structure of the reciprocating booster compressor which concerns on 4th Embodiment. It is sectional drawing which shows the structure of the reciprocating booster compressor which concerns on 5th Embodiment.

Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described in the embodiments or shown in the drawings are not intended to limit the scope of the present invention, but are merely illustrative examples. Absent.
For example, expressions expressing relative or absolute arrangements such as “in a certain direction”, “along a certain direction”, “parallel”, “orthogonal”, “center”, “concentric” or “coaxial” are strictly In addition to such an arrangement, it is also possible to represent a state of relative displacement with an angle or a distance such that tolerance or the same function can be obtained.
In addition, for example, expressions representing shapes such as quadrangular shapes and cylindrical shapes not only represent shapes such as quadrangular shapes and cylindrical shapes in a strict geometric sense, but also within the range where the same effect can be obtained. A shape including a chamfered portion or the like is also expressed.
On the other hand, the expressions “comprising”, “comprising”, “comprising”, “including”, or “having” one constituent element are not exclusive expressions for excluding the existence of the other constituent elements.

<First Embodiment>
FIG. 1 is a cross-sectional view showing a configuration of a reciprocating booster compressor (hereinafter referred to as “compressor” as appropriate) according to the first embodiment. The compressor 1 is an oil-free reciprocating compressor, and pressurized gas higher than atmospheric pressure is introduced from an external gas supply source (not shown) through a first passage 2 that is a supply pipe. . The compressor 1 compresses the pressurized gas introduced from the first passage 2 in a plurality of cylinders (first cylinder LP and second cylinder HP) connected in series with each other, and is discharged from the discharge pipe 4 to the outside. It discharges toward the supply destination (not shown).
In the following description, the oil-free compressor 1 is mainly described. However, the oil-free compressor 1 is applicable unless otherwise specified.

The compressor 1 has an input shaft 5 that can be rotationally driven by power input from an external power source (not shown) such as an electric motor. The input shaft 5 is formed integrally with a crankshaft 10 constituting a crank mechanism 8 housed in a crankcase 6 provided at the lower portion of the compressor 1. The crankshaft 10 is rotatably supported by

bearings

12 and 14 provided in the crankcase 6. Further, the crankcase 6 has the input shaft 5 passing through on the bearing 12 side, and the inside of the crankcase 6 is tightly sealed with respect to the outside by a seal member 16.

One end of connecting

rods

18 and 20 corresponding to the first cylinder LP and the second cylinder HP provided above the crankcase 6 is pivotally supported on the crankshaft 6 via

seal members

22 and 24, respectively. ing. The other ends of the connecting

rods

18 and 20 are pivotally supported by

pistons

30 and 32 inserted into the

cylinders

26 and 28 constituting the first cylinder LP and the second cylinder HP.
Since the compressor 1 is an oil-free type, in order to suppress leakage from the compression chamber, for example, a composite piston (composite resin piston) is used as the

pistons

30 and 32, and a piston ring abutment not shown is compressed. Sometimes, a method of fixing at a position where theoretical leakage is not possible is adopted.

Further, a partition wall 34 is provided on the inner wall of the crankcase 6. Thereby, the inside of the crankcase 6 is divided into a first space 36 corresponding to the first cylinder LP and a second space 38 corresponding to the second cylinder HP. The partition wall 34 is formed with an opening 40 through which the crankshaft 10 configured integrally with the input shaft 5 passes. The opening 40 is provided with a sealing member 42 for sealing the opening 40 while the crankshaft 10 is rotatably supported. Accordingly, the first space 36 and the second space 38 are separated from each other by the partition wall 34 provided inside the crankcase 6.

The first cylinder LP has an intake chamber 46 having an inlet for introducing intake air on the top wall of the cylinder 26 and a guide for discharging the first pressurized gas compressed by the first cylinder LP. An air discharge chamber 50 having an outlet is defined by a partition wall 52. The intake chamber 46 and the exhaust chamber 50 communicate with the inside of the cylinder 26 through an intake port 53 and an exhaust port 54. The intake port 53 and the exhaust port 54 are each provided with a backflow prevention valve (not shown).

The second cylinder HP has, on the top wall of the cylinder 28, an intake chamber 58 having an inlet for introducing intake air, and a guide for discharging the second pressurized gas compressed in the second cylinder HP. An air discharge chamber 62 having an outlet is defined by a partition wall 64. The intake chamber 58 and the exhaust chamber 62 communicate with the cylinder 28 through an intake port 66 and an exhaust port 68. The intake port 66 and the exhaust port 68 are each provided with a backflow prevention valve (not shown).

The first passage 2 to which the pressurized gas is supplied is connected so as to communicate with the first space 36 in the crankcase 6, and the first space 36 is connected to the first passage 36 via the second passage 70. Connected to the suction side of one cylinder LP. Therefore, the pressurized gas supplied from the first passage 2 is sucked into the first cylinder LP through the first space 36. As a result, the first space 36 is pressurized to approximately the same pressure as the intake chamber 46 by the pressurized gas. As a result, the pressure difference between the first space 36 and the intake chamber 46 is reduced, and the load on the first cylinder LP during driving is reduced.

The discharge side of the first cylinder LP is connected to the second space 38 in the crankcase 6 by the third passage 72, and the second space 38 is connected to the second cylinder HP by the fourth passage 74. Connected to the intake side. Therefore, the first pressurized gas discharged from the first cylinder LP is sucked into the second cylinder HP through the second space 38. As a result, the second space 38 is pressurized to a pressure substantially equal to that of the intake chamber 58 by the first pressurized gas. As a result, the pressure difference between the second space 38 and the intake chamber 58 is reduced, and the load on the second cylinder HP during driving is reduced. Note that an intermediate cooler (not shown) may be provided in the third passage 72.

Here, since the first space 36 and the second space 38 are separated from each other by the partition wall 34, the first space 36 and the second space 38 can form independent pressures. Thus, the crankcase 6 can be divided into a plurality of spaces corresponding to each cylinder and set to a pressure corresponding to each cylinder, so that the pressure difference from the crankcase 6 side is appropriately suppressed in each cylinder. be able to. Therefore, it is possible to reduce the load applied to components such as the

bearings

12 and 14 of the crankshaft 10 constituting the crank mechanism 8, and to achieve a long product life. Furthermore, a high energy saving effect can be obtained.

FIG. 2 is a modification of FIG. As shown in FIG. 2, the third passage 72 is made of a tubular member through which the first pressurized gas discharged from the first cylinder LP passes, and heat radiating fins 76 are provided on the outer surface thereof. Yes. Since the first pressurized gas discharged from the first cylinder LP has a high temperature, it is preferably cooled when supplied to the second cylinder HP on the high pressure side. Conventionally, such a high-temperature compressed gas from the low-pressure side has often been performed using an external device such as an intercooler, but in the present embodiment, the radiating fins 76 are formed on the outer surface of the third passage 72. By providing, the first pressurized gas can be effectively cooled when passing through the third passage 72. Thereby, when an intermediate cooler (not shown) is provided between the first cylinder LP and the second cylinder HP, the intermediate cooler can be reduced in size. Alternatively, if the cooling effect by the radiating fins 76 is sufficient, there is no need to provide an intermediate cooler. As a result, the apparatus can be reduced in size.

Further, the third passage 72 is connected between the partition wall 34 and the second cylinder HP in the crankcase 6, and an outlet side thereof opens toward the seal member 42. Since the seal member 42 seals the opening 32 provided in the partition wall 34 while rotatably supporting the crankshaft 10, the seal member 42 tends to become high temperature during driving. Therefore, the first pressurized air introduced into the first space 36 is jetted toward the seal member 42 with respect to the seal member 42, so that the seal member 42 is pressurized together with the second space 38. Can be cooled. In particular, when the heat dissipating fins 76 are provided in the third passage 72 as shown in FIG. 2, since the first pressurized gas after cooling can be supplied from the third passage 72, the seal member 42 can be cooled more effectively.

The first passage 2 is also connected between the partition wall 34 and the first cylinder LP in the crankcase 6 in the same manner as the third passage 72 described above, and its outlet side opens toward the seal member 42. You may comprise. As described above, also in the first space 36, the introduced pressurized gas is jetted toward the seal member 42, so that the seal member 42 can be cooled together with the pressurization of the first space 36.

In particular, when both the first passage 2 and the third passage 72 are configured so that the outlet sides thereof open toward the seal member 42, the seal member 42 has both sides (first space 36 and second space 38). Therefore, the temperature can be more effectively suppressed.

Second Embodiment
FIG. 3 is a cross-sectional view showing a configuration of a reciprocating booster compressor (hereinafter referred to as “compressor” as appropriate) according to the second embodiment. In FIG. 3, the components corresponding to those of the first embodiment described above are denoted by the same reference numerals, and redundant descriptions are omitted as appropriate.

In the second embodiment, the discharge-side exhaust chamber 50 of the first cylinder LP is connected to the intake-side intake chamber 58 of the second cylinder HP by a fifth passage 82. That is, in the first embodiment, the exhaust side of the first cylinder LP is connected to the intake side of the second cylinder HP via the second space 38, but in the second embodiment, the second space It is directly connected without going through 38.

Then, a sixth passage 86 connected to the second space 38 branches from a branch point 84 in the middle of the fifth passage 82. As a result, a part of the first pressurized gas flowing through the fifth passage 82 is supplied to the second space 38 via the sixth passage 86. Thus, since the sixth passage 86 can be designed independently of the fifth passage 82 for supplying the first pressurized gas to the second cylinder HP, a more flexible device configuration can be obtained.

The sixth passage 86 connected to the second space 38 may be provided with radiating fins 76 on the outer surface thereof, similarly to the third passage 72 shown in FIG. Thereby, the 1st pressurized gas supplied to the 2nd space 38 can be cooled, and the cooling effect of the 2nd space 38 (especially seal member 42) can be heightened.

Further, the sixth passage 86 connected to the second space 38 is also the first passage supplied from the sixth passage 86 to the second space 38 in the same manner as the third passage 72 of the first embodiment. The pressurized gas may be configured to be injected from the second space 38 side toward the seal member 42 provided in the partition wall 34. Also in this case, the first pressurized gas supplied from the sixth passage 86 is supplied to the seal member 42, so that the seal member 42 is effectively cooled.

<Third Embodiment>
FIG. 4 is a cross-sectional view showing a configuration of a reciprocating booster compressor according to the third embodiment. In FIG. 4, components corresponding to the above-described embodiments are denoted by common reference numerals, and redundant descriptions are omitted as appropriate.

In the present embodiment, the first pressurized gas discharged from the first cylinder LP is introduced into the first space 36. The first pressurized gas introduced into the first space 36 has a pressure that is at least higher than that of the first space 36. In the example of FIG. 4, the first pressurized gas supplied to the first space 36 is from a fifth passage 82 that connects the discharge side of the first cylinder LP and the intake side of the second cylinder HP. It is configured to be introduced through a sixth passage 86 that branches.

A pressure reducing valve for adjusting the pressure of the first pressurized gas to an appropriate value is disposed on the sixth passage 86 for supplying the first pressurized gas to the first space 36. It may be. Accordingly, the first space 36 is pressurized using the first pressurized gas discharged from the first cylinder LP, so that the first space 36 is interposed between the first cylinder LP and the first space 36. The pressure difference can be suppressed.

The second pressurized gas discharged from the second cylinder HP is introduced into one second space 38. The second pressurized gas introduced into the second space 38 has a pressure that is at least higher than that of the second space 38. In the example of FIG. 4, the second pressurized gas supplied to the second space 38 is configured to be introduced through a seventh passage 88 branched from the discharge pipe 4 of the second cylinder HP. ing.

A pressure reducing valve for adjusting the pressure of the second pressurized gas to an appropriate value is disposed on the seventh passage 88 for supplying the first pressurized gas to the second space 38. It may be. Accordingly, the second space 38 is pressurized using the second pressurized gas discharged from the second cylinder HP, so that the space between the second cylinder HP and the second space 38 is increased. The pressure difference can be suppressed.

<Fourth embodiment>
FIG. 5 is a cross-sectional view showing a configuration of a reciprocating booster compressor according to the fourth embodiment. In FIG. 5, components corresponding to the above-described embodiments are denoted by common reference numerals, and redundant descriptions are omitted as appropriate.

In the present embodiment, the pressurized gas supplied from the first passage (supply pipe) 2 is introduced into the first space 36 as in the first and second embodiments described above. Thereby, the first space 36 is pressurized using the pressurized gas supplied from the supply pipe 2, thereby suppressing a pressure difference between the first cylinder LP and the first space 36. Can do.

The second pressurized gas discharged from the second cylinder HP is introduced into one second space 38. The second pressurized gas introduced into the second space 38 has a pressure that is at least higher than that of the second space 38. In the example of FIG. 5, as in the third embodiment described above, the second pressurized gas supplied to the second space 38 is the seventh passage 88 branched from the discharge pipe 4 of the second cylinder HP. It is comprised so that it may be introduced via.

<Fifth Embodiment>
FIG. 6 is a cross-sectional view showing a configuration of a reciprocating booster compressor according to the fifth embodiment. In FIG. 6, components corresponding to the above-described embodiments are denoted by common reference numerals, and redundant descriptions are omitted as appropriate.

In the present embodiment, the second pressurized gas discharged from the second cylinder HP is introduced into the first space 36. The second pressurized gas introduced into the first space 36 has a pressure that is at least higher than that of the first space 36. In the example of FIG. 6, the second pressurized gas supplied to the first space 36 is configured to be introduced through an eighth passage 90 branched from the discharge pipe 4 of the second cylinder HP. ing.

A pressure reducing valve for adjusting the pressure of the second pressurized gas to an appropriate value is disposed on the eighth passage 90 for supplying the second pressurized gas to the first space 36. It may be. Thus, the first space 36 is pressurized using the second pressurized gas discharged from the second cylinder HP, so that the first space 36 is interposed between the first cylinder LP and the first space 36. The pressure difference can be suppressed.

The second pressurized gas discharged from the second cylinder HP is introduced into one second space 38. The second pressurized gas introduced into the second space 38 has a pressure that is at least higher than that of the second space 38. In the example of FIG. 6, as in the third and fourth embodiments described above, the second pressurized gas supplied to the second space 38 is branched from the discharge pipe 4 of the second cylinder HP. It is configured to be introduced through the passage 88.

As described above, according to the above embodiment, in each cylinder that performs multi-stage compression, it is possible to achieve a long life and obtain a high energy saving effect by appropriately setting the internal pressure of the crankcase. A reciprocating booster compressor can be provided.

At least one embodiment of the present invention can be used in a reciprocating booster compressor capable of further compressing pressurized gas supplied from the outside by reciprocating movement of a piston in a cylinder.

1 Compressor 2 First passage (supply pipe)
4 Discharge pipe 5 Input shaft 6 Crankcase 8 Crank mechanism 10

Crankshaft

12, 14

Bearing

16, 22, 24, 42

Seal member

18, 20 Connecting

rod

26, 28

Cylinder

30, 32 Piston 34 Partition 36 First space 38 First 2 space 70 2nd passage 72 3rd passage 74 4th passage 76 Radiation fin 82 5th passage 86 6th passage 88 7th passage 90 8th passage LP 1st cylinder HP 2nd cylinder

Claims

A crank mechanism for converting the rotational motion of the input shaft to which power is input into reciprocating motion;
A crankcase that houses the crank mechanism;
A plurality of cylinders capable of compressing gas by being driven by a reciprocating motion converted by the crank mechanism;
With
The plurality of cylinders are
A first cylinder that generates a first pressurized gas having a pressure higher than that of the pressurized gas by compressing the pressurized gas supplied from the outside;
A second cylinder connected in series to the first cylinder and generating a second pressurized gas higher in pressure than the first pressurized gas by further compressing the first pressurized gas;
Including
The crankcase includes a first space corresponding to the first cylinder and a second space corresponding to the second cylinder;
The first space and the second space are separated from each other by a partition wall provided inside the crankcase,
At least one of the first space and the second space is pressurized by introducing any one of the pressurized gas, the first pressurized gas, and the second pressurized gas. , Reciprocating booster compressor.
The pressurized gas is introduced into the first space,
The reciprocating booster compressor according to claim 1, wherein the first pressurized gas is introduced into the second space.
A first passage connecting the inlet of the pressurized gas and the first space;
A second passage connecting the first space and the suction side of the first cylinder;
The reciprocating booster compressor according to claim 2, comprising:
A third passage connecting the discharge side of the first cylinder and the second space;
A fourth passage connecting the second space and the suction side of the second cylinder;
A reciprocating booster compressor according to claim 2, comprising:
The reciprocating booster compressor according to claim 4, wherein heat radiation fins are provided on an outer surface of the third passage.
A fifth passage connecting the discharge side of the first cylinder and the suction side of the second cylinder;
A sixth passage branched from the fifth passage and connected to the second space;
A reciprocating booster compressor according to claim 2, comprising:
The reciprocating booster compressor according to claim 6, wherein heat radiation fins are provided on an outer surface of the sixth passage.
The partition is
An opening through which the input shaft passes;
A seal member that seals the opening while the input shaft is rotatably supported;
A reciprocating booster compressor according to any one of claims 1 to 7, comprising:
The reciprocating booster compressor according to claim 8, wherein the first space is configured such that the pressurized air introduced into the first space is injected toward the seal member.
The reciprocating type according to claim 8 or 9, wherein the second space is configured such that the first pressurized air introduced into the second space is jetted toward the seal member. Booster compressor.
The first pressurized gas is introduced into the first space,
The reciprocating booster compressor according to claim 1, wherein the second pressurized gas is introduced into the second space.
The pressurized gas is introduced into the first space,
The reciprocating booster compressor according to claim 1, wherein the second pressurized gas is introduced into the second space.
The reciprocating booster compressor according to claim 1, wherein the second pressurized gas is introduced into the first space and the second space.
The reciprocating booster compressor according to any one of claims 1 to 13, which is an oil-free compressor.