JP4210206B2 - Reciprocating compressor - Google Patents

Description

  The present invention relates to a reciprocating compressor that compresses a gas such as hydrogen or helium and supplies the compressed gas to a supply destination.

  As reciprocating compressors, for example, two examples having a configuration as described later are known. First, a reciprocating compressor according to Conventional Example 1 will be described with reference to FIG. That is, a first chamber 53, a second chamber 54, and a third chamber 55 that are adjacent to each other from the cylinder 51 side are provided between the cylinder 51 and the crankcase 52, and a piston rod 56 passes through each of these chambers. A connection cylinder 57 is formed. The partition walls between the cylinder 51, the first chamber 53, the second chamber 54, the third chamber 55, and the crankcase 52 include first, second, third, and fourth shaft seal devices 58, 59, 60. , 61 are provided. Further, a communication path 66 that communicates from the inside of the first shaft seal device 58 to the suction flow path 65 is provided. The first chamber 53 is filled with an inert gas. When the inert gas enters the first shaft sealing device 58, the first chamber 53 is returned to the suction flow path 65 through the communication path 66. Has been. In addition, an oil bath 68 in which oil is sealed so as to immerse the piston rod 56 at a pressure slightly higher than the pressure of the inert gas sealed in the first chamber 53 and the periphery thereof are surrounded in the second chamber 54. By providing a cooling water jacket 69 for cooling the oil, the second shaft sealing device 59 and the third shaft sealing device 60 are of the oil bath type.

  According to the reciprocating gas compressor configured as described above, the following effects can be obtained. (1) As a result of all the shaft seal devices being able to follow the runout of the piston rod, the runout prevention device is not required, and the compressor can be used for a long time. (2) Since the inert gas having a pressure slightly higher than the suction pressure is only sealed in the first chamber, the sealing performance of the oil bath type shaft seal device in the second chamber can be improved, and the communication path Leakage gas can be prevented from entering the first chamber, and the connecting cylinder, oil, and crankcase can be kept clean without touching the handling gas. (3) Since pressure is applied to the oil in the oil bath type shaft seal device, the inert gas sealed in the first chamber is prevented from leaking into the oil, and the pressure of the sealed gas in the first chamber should be Even if the leaked gas enters the first chamber, the leaked gas can be completely sealed by the oil pressure of the oil bath type shaft seal device (see, for example, Patent Document 1). ).

  The configuration of the reciprocating compressor according to Conventional Example 2 will be described with reference to FIG. Unlike the conventional example 1, the conventional example 2 is not provided with a plurality of shaft sealing devices such as the first, second, third, and fourth shaft sealing devices, and instead of these shaft sealing devices. A rod packing and an oil draining member are provided. More specifically, a cross guide mechanism 72 is provided between the cylinder 71 and the crankcase 73, and a distance piece 74 is provided between the cylinder 71 and the cross guide mechanism 72. The cross guide mechanism 72 connects the connecting rod connected to the crankshaft of the crankcase 73 and the piston rod 75, and reciprocates when the crankshaft rotates. The crosshead 72a reciprocates. And a cylindrical crosshead guide 72b for guiding in this manner. Further, on the cylinder 71 side of the distance piece 74, a rod packing 76 into which a piston rod 75 penetrating the distance piece 74 is slidably fitted is provided. Further, an oil draining member 77 into which a piston rod 75 penetrating the distance piece 74 is slidably fitted is provided on the distance piece 74 on the cross guide mechanism 72 side.

The rod packing 76 partitions the right crank side chamber 71c in the drawing and the distance piece 74, which is partitioned by the piston 71a of the cylinder 71, and blocks the gas flow between the two. . The oil draining member 77 functions to prevent oil from moving from the crankcase 73 side to the cylinder 71 side and to prevent oil from being mixed into the compressed gas. However, since the oil draining member 77 does not block the flow of gas, the distance piece 74 and the cross guide mechanism 72 (and the crankcase 73) have substantially the same pressure. The crankcase 73 is opened to the air space through the air opening hole 73a, and the distance piece 74 and the cross guide mechanism 72 are at atmospheric pressure as in the crankcase 73 (see Non-Patent Document 1).
Japanese Patent Publication No. 7-88814 (Fig. 1) Heinz P. Bloch AND John J. Hoefner, “Reciprocating Compressors”, Gulf Publishing Company (Houston, Texas). 1996

  However, the reciprocating compressors of Conventional Example 1 and Conventional Example 2 described above are provided with a piston-type compressor mechanism, and the suction pressure suitable for this compressor mechanism is generally a low pressure of about 1 MPa or less. In order to obtain a gas having a high pressure of, for example, about 100 MPa as obtained by a diaphragm compressor as the pressure, for example, it is necessary to prepare a plurality of reciprocating compressors and connect the compression chambers. . However, in the case of such a configuration, an increase in the size of the entire compressor is unavoidable, and it is not possible to sufficiently cope with installation space restrictions.

  On the other hand, in a diaphragm compressor, although a gas having a high pressure of about 100 MPa can be obtained, for example, a suction pressure of 10 MPa or more is necessary as a suction pressure, and a low pressure such as a suction pressure suitable for a piston compressor is required. In this case, it cannot be applied, and it is considered that some boosting means is necessary on the suction side.

  Therefore, the present invention avoids an increase in the size of the entire compressor, and even if the suction pressure is a low pressure such as a suction pressure suitable for a piston type compressor, the discharge pressure is high enough to be obtained by a diaphragm compressor. It is an object of the present invention to provide a reciprocating compressor capable of obtaining a pressure gas.

  The present invention for solving the above-described problems is configured as follows.

  The invention according to claim 1 is a crankcase having a crankshaft that is rotationally driven, a cylinder in which a piston is housed and a compression chamber is formed, and a cross guide mechanism provided between the crankcase and the cylinder A piston rod that reciprocates by connecting the crankshaft and the piston via a cylinder, and a partition that separates the cylinder and the cross guide mechanism, and the piston rod that passes through the partition is slidably fitted. An oil draining member to be inserted, a diaphragm that compresses gas by reducing the volume of the diaphragm compression chamber, and a cross guide mechanism that is different from the cross guide mechanism, are connected to the crankshaft of the crankcase, and the diaphragm is A diaphragm rod that reciprocates, and gas discharged from the compression chamber of the cylinder It is configured to be discharged to the outside through Fulham compression chamber, and the partition wall side of the space of the suction line and the cylinder of the cylinder is a reciprocating compressor, characterized in that are communicated.

  According to a second aspect of the present invention, in the reciprocating compressor according to the first aspect, a plurality of the compression chambers are formed in the cylinder by providing a plurality of the pistons at intervals to the piston rod. The compression chambers of the plurality of compression chambers are connected to each other, and the pressure is increased as the gas communicates with the compression chambers located further away from the crankcase. The gas discharged from a certain compression chamber is configured to be discharged outside through the diaphragm compression chamber.

  According to the reciprocating compressor of claim 1 or 2, the piston-type compressor mechanism and the diaphragm-type compressor mechanism are connected, and the gas discharged from the compression chamber of the suction side cylinder is externally passed through the diaphragm-compression chamber. Suitable for compression by the diaphragm from the cylinder compression chamber to the diaphragm compression chamber even if the suction pressure is a low pressure such as the suction pressure suitable for a piston compressor. Since a gas having a suction pressure can be supplied, a gas having a high pressure such that the discharge pressure can be obtained with a diaphragm compressor can be obtained. Further, a single drive source composed of a crankcase having a crankshaft is configured to drive a piston that reciprocates in the cylinder and a reciprocating diaphragm that compresses gas by reducing the volume of the diaphragm compression chamber. Therefore, it is possible to avoid an increase in the size of the entire compressor, and it is possible to save space as compared with the case where the piston compressor and the diaphragm compressor are separately prepared.

  In the reciprocating compressor according to claim 1 or 2, the partition wall separating the cylinder and the cross guide mechanism is provided with an oil draining member into which a piston rod penetrating the partition wall is slidably fitted, and suction of the cylinder The line is configured to communicate with the space on the partition side of the cylinder. As a result, the space inside the crankcase, the cross guide mechanism, and the space on the partition wall side of the cylinder can be maintained at a uniform pressure, and the release of gas to the outside that reduces the efficiency of the compressor can be avoided.

  According to the reciprocating compressor of claim 2, since the multi-stage compression structure has a plurality of compression chambers in a single cylinder on the suction side, the suction pressure has a lower pressure such as atmospheric pressure. Even in this case, a gas having a suction pressure suitable for compression by the diaphragm can be supplied from the compression chamber at the final stage of the cylinder to the diaphragm compression chamber, so that the discharge pressure is high enough to be obtained by the diaphragm compressor. Gas can be obtained. Moreover, since the members having sliding portions such as the piston rod and the cross guide mechanism are not increased from those of the single-stage compression structure, an increase in maintenance load of these members can be avoided.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a diagram showing an overall configuration of a reciprocating compressor according to a first embodiment of the present invention.

  As shown in FIG. 1, the reciprocating compressor of the first embodiment includes a crankcase 3 having a crankshaft 3 a that is driven to rotate, a cylinder 1, and a cross provided between the crankcase 3 and the cylinder 1. The piston rod 5 is connected to the crankshaft 3a via the guide mechanism 2 and reciprocates. The cross guide mechanism 2 connects the connecting rod 3b connected to the crankshaft 3a and the piston rod 5, and reciprocates by the rotational drive of the crankshaft 3a, and the crosshead 2a reciprocates. And a cylindrical crosshead guide 2b that guides the head. Further, the partition wall 4 separating the cylinder 1 and the cross guide mechanism 2 is provided with an oil draining member 6 into which a piston rod 5 penetrating the partition wall 4 is slidably fitted.

  In the cylinder 1, the 1st piston 1a provided in the piston rod 5 reciprocates. Then, in the first compression chamber 1c, which is a space on the left side in FIG. 1 and partitioned by the first piston 1a of the cylinder 1, an inlet side check is made in such a direction as to permit the inflow of gas to the first compression chamber 1c side. The suction line 7 in which the valve 7a is interposed communicates. Further, a communication line 8 communicates between the inlet check valve 7a of the suction line 7 and the cylinder 1 from a partition side chamber 1d which is a right space in FIG. 1 and is partitioned by a first piston 1a. .

  The reciprocating compressor of the first embodiment includes a diaphragm 12 that compresses gas by reducing the volume of the diaphragm compression chamber 14, and further includes a cross guide mechanism 11 that is different from the cross guide mechanism 2. A diaphragm rod 13 that is connected to the crankshaft 3a of the crankcase 3 and reciprocates the diaphragm 12 is provided. The cross guide mechanism 11 connects the connecting rod 3c connected to the crankshaft 3a and the diaphragm rod 13 and reciprocates by the rotational drive of the crankshaft 3a, and the crosshead 11a reciprocates. And a cylindrical crosshead guide 11b for guiding in this manner. The diaphragm 12 performs gas compression by reducing the volume of the diaphragm compression chamber 14 by reciprocating the substantially central portion of the diaphragm 12 along with the reciprocating movement of the diaphragm rod 13.

  The first compression chamber 1c of the cylinder 1 and the diaphragm compression chamber 14 communicate with each other through an intermediate line 9 in which an intermediate check valve 9a is interposed. The intermediate check valve 9 a is provided in a direction that allows the flow of compressed gas from the first compression chamber 1 c to the diaphragm compression chamber 14. Further, a discharge line 10 in which an outlet check valve 10a is interposed is provided on the supply side of the compressed gas (not shown) from the diaphragm compression chamber 14 in a direction allowing the flow of the compressed gas to the supply side. .

  The reciprocating compressor of the first embodiment is configured in this way, and the piston type compressor mechanism is provided with an oil draining member 6, but is different from the reciprocating compressor of the conventional example 1. A large number of shaft sealing devices are not provided, and unlike the reciprocating compressor of the conventional example 2, no rod packing, distance piece or the like is provided, and the structure is extremely simple. In this reciprocating compressor, the gas can freely flow between the partition side chamber 1d of the cylinder 1, the cross guide mechanism 2, and the crankcase 3. The presence of the oil draining member 6 causes a slight pressure difference between the partition side chamber 1d sandwiching the oil draining member 6 and the cross guide mechanism 2, but a certain time has elapsed during steady operation or after the operation is stopped. Thereafter, the pressure in the partition side chamber 1d, the cross guide mechanism, and the crankcase 3 of the cylinder 1 is uniform.

  Next, the operation of the reciprocating compressor of the first embodiment configured as described above will be described. For example, a gas having a suction pressure of 1 MPa is supplied from the suction line 7 of the cylinder 1 to the first compression chamber 1c by the operation of the reciprocating compressor, and the gas having a pressure of, for example, 10 MPa is compressed in the first compression chamber 1c. Is supplied to the diaphragm compression chamber 14 via the intermediate line 9. The gas supplied to the diaphragm compression chamber 14 is compressed into a gas having a high discharge pressure of, for example, 100 MPa by the compression operation of the diaphragm 12, and the high pressure gas compressed in the diaphragm compression chamber 14 passes through the discharge line 10. To the supply side.

  As described above, the reciprocating compressor according to the first embodiment connects the piston-type compressor mechanism and the diaphragm-type compressor mechanism, and the gas discharged from the first compression chamber 1c of the cylinder 1 on the suction side. Is discharged to the outside through the diaphragm compression chamber 14. Thereby, even if the suction pressure is a low pressure of 1 MPa or less, such as the suction pressure suitable for a piston compressor, the diaphragm compression chamber 14 is suitable for compression by the diaphragm 12 from the first compression chamber 1c of the cylinder 1, for example. Since a gas having a suction pressure of 10 MPa or more can be supplied, a gas having a high pressure of, for example, 100 MPa that can be obtained by a diaphragm compressor can be obtained.

  In addition, a piston 5 that reciprocates in the cylinder 1 and a diaphragm 12 that reciprocates to compress gas by reducing the volume of the diaphragm compression chamber 14 by a single drive source including a crankcase 3 having a crankshaft 3a. Since it is configured to be driven, it is possible to avoid an increase in the size of the entire compressor, and it is possible to save space as compared with the case where the piston compressor and the diaphragm compressor are separately prepared. .

  The partition wall 4 separating the cylinder 1 and the cross guide mechanism 2 is provided with an oil draining member 6 into which a piston rod 5 penetrating the partition wall 4 is slidably fitted, and the suction line 7 of the cylinder 1 and the cylinder 1 A communication line 8 is provided to communicate with the partition side chamber 1d. As a result, during steady operation, the crankcase 3, the crosshead guide 2b, and the partition side chamber 1d can be maintained at a uniform pressure, and the release of gas to the outside that reduces the efficiency of the compressor can be avoided.

  Next, a second embodiment of the present invention will be described. FIG. 2 is a diagram showing an overall configuration of a reciprocating compressor according to a second embodiment of the present invention. Here, in the present embodiment, the same parts as in the reciprocating compressor of the first embodiment shown in FIG. 1 are denoted by the same reference numerals as in FIG. To do.

  In the reciprocating compressor of the second embodiment, as shown in FIG. 2, the cylinder 1 ′ has a large diameter portion and a small diameter portion in this order from the crankcase 3 side, and is provided on the piston rod 5 ′. The first piston 1a reciprocates within the large diameter portion, and the second piston 1b provided on the piston rod 5 'reciprocates within the small diameter portion. Thus, in the cylinder 1 ′, the first compression chamber 1c, which is the space on the left side in FIG. 2, partitioned by the first piston 1a of the cylinder 1 ′, and the first compression chamber 1c further in FIG. A second compression chamber 1e, which is the left space, is formed.

  The first compression chamber 1c and the second compression chamber 1e communicate with each other through an intermediate line 9 'in which an intermediate check valve 9a' is interposed. The intermediate check valve 9a 'is provided in a direction that allows the flow of compressed gas from the first compression chamber 1c to the second compression chamber 1e. Further, the diaphragm compression chamber 14 and the second compression chamber 1e at the final stage located farthest from the crankcase 3 are communicated with each other by a second intermediate line 15 in which a second intermediate check valve 15a is interposed. Yes.

  Next, the operation of the reciprocating compressor of the second embodiment configured as described above will be described. By the operation of the reciprocating compressor, for example, a gas having a suction pressure of about 0.1 MPa, which is about atmospheric pressure, is supplied to the first compression chamber 1c from the suction line 7 of the cylinder 1 ′, and is compressed in the first compression chamber 1c. For example, a gas having a pressure of 1 MPa is supplied to the second compression chamber 1e through the intermediate line 9 ′. The gas supplied to the second compression chamber 1e is compressed into a gas having a pressure of, for example, 10 MPa by the compression operation by the second piston 1b, and the gas having a pressure of 10 MPa is compressed through the second intermediate line 15 to the diaphragm compression chamber. 14. The gas supplied to the diaphragm compression chamber 14 is compressed into a gas having a high discharge pressure of, for example, 100 MPa by the compression operation of the diaphragm 12, and the high pressure gas compressed in the diaphragm compression chamber 14 passes through the discharge line 10. To the supply side.

  As described above, according to the reciprocating compressor of the second embodiment, the multi-stage compression structure having the plurality of compression chambers 1c and 1e in the single cylinder 1 ′ on the suction side has the suction pressure. Is suitable for compression by the diaphragm 12 from the compression chamber 1e at the final stage of the cylinder 1 'to the diaphragm compression chamber 14 even when the suction pressure is suitable for a piston type compressor, for example, at a lower pressure of about atmospheric pressure. For example, since a gas having a suction pressure of 10 MPa or more can be supplied, it is possible to obtain a gas having a high pressure of 100 MPa, for example, such that the discharge pressure can be obtained by a diaphragm compressor. Further, since the number of members having sliding portions such as a piston rod and a cross guide mechanism is not increased from that of the single-stage compression structure such as the reciprocating compressor of the first embodiment, the maintenance load accompanying these members is increased. Can be avoided.

  In the first and second embodiments of the present invention, the piston-type compressor mechanism and the diaphragm-type compressor mechanism are horizontally arranged. However, the present invention is not limited thereto. For example, a piston type compressor mechanism may be arranged at the upper part of the crankcase. Depending on the installation space, the piston-type compressor mechanism and the diaphragm-type compressor mechanism may be arranged at free positions.

It is a figure showing the whole reciprocating compressor composition by a 1st embodiment of the present invention. It is a figure which shows the whole structure of the reciprocating compressor by 2nd Embodiment of this invention. It is a figure which shows the whole structure of the reciprocating compressor of the prior art example 1. FIG. It is a figure which shows the whole structure of the reciprocating compressor of the prior art example 2.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,1 '... Cylinder 1a ... 1st piston 1b ... 2nd piston 1c ... 1st compression chamber 1d ... Partition wall side chamber 1e ... 2nd compression chamber 2 ... Cross guide mechanism 3 ... Crankcase 3a ... Crankshaft 3b, 3c ... Connection Rod 4 ... Bulkhead 5, 5 '... Piston rod 6 ... Oil draining member 7 ... Suction line 8 ... Communication line 9, 9' ... Intermediate line 10 ... Discharge line 11 ... Cross guide mechanism 12 ... Diaphragm 13 ... Diaphragm rod 14 ... Diaphragm compression chamber 15 ... Second intermediate line

Claims (2)

  A crankcase having a crankshaft that is driven to rotate, a cylinder in which a piston is housed and a compression chamber is formed, and the crankshaft via a cross guide mechanism provided between the crankcase and the cylinder. A piston rod that reciprocates by connecting the piston, an oil draining member that is provided in a partition wall that separates the cylinder and the cross guide mechanism, and into which the piston rod penetrating the partition wall is slidably inserted; A diaphragm that compresses gas by reducing the volume of the diaphragm compression chamber; a diaphragm rod that is connected to the crankshaft of the crankcase via a cross guide mechanism that is different from the cross guide mechanism, and reciprocates the diaphragm; Gas discharged from the compression chamber of the cylinder passes through the diaphragm compression chamber. Is configured to be discharged to the outside Te, reciprocating compressor and the partition wall side of the space of the suction line and the cylinder of said cylinder characterized in that it communicates with. The reciprocating compressor according to claim 1, wherein a plurality of the compression chambers are formed in the cylinder by providing a plurality of the pistons at an interval to the piston rod, and the plurality of compression chambers are communicated with each other. And the gas is configured to have a higher pressure as it goes to the compression chamber located further away from the crankcase, and is discharged from the compression chamber located farthest from the crankcase in the plurality of compression chambers. A reciprocating compressor characterized in that gas is discharged to the outside through the diaphragm compression chamber.