Oilless reciprocating compressor and expansion apparatus

Abstract: A piston (10) movable in a metal cylinder of an oilless reciprocating compressor and expansion apparatus comprises a piston body (10A) to which a piston ring made of a self-­ lubricating material is fitted. The piston body is made, either fully or on its circumferential surface side, of self-­ lubricating material (10B) without influencing adversely the durability of the piston itself by the compression heat at the piston top. Alternatively, a ring groove formed into the shape of the letter C whose ends are spaced apart may be provided in the circumferential surface of the piston which has at least its surface side made of self-lubricating material, and said ring groove is positioned on the side thrust line orthogonal to the piston pin, so that the compression efficiency is improved.

Description: The present invention relates to an oilless reciprocating compressor and an oilless reciprocating expansion apparatus, and in particular to an oilless reciprocating compressor and an oilless reciprocating expansion apparatus each comprising a piston body to which a piston ring made of a self-lubricating material is fitted. Conventionally, oilless compressors and oil less expansion apparatuses are known which are constructed in such a manner that, in order to secure smooth slidability between the piston and the cylinder, for example, as shown in Fig. 3, multi-stage ring grooves 111a, 111b, 111c are formed almost throughout the outer circumferential surface from the top side of the piston 101 made of aluminum or other metal material to the skirt side, piston rings 105a, 105b and a rider ring 106 made of fluorocarbon resin or other self-lubricating resin are put in said ring grooves, and the outer diameter of the rings is set slightly larger than the outer diameter of the land section 102 (a ringlike projection for supporting the piston rings in the upper and lower ring grooves), so that only the self-lubricating piston rings 105a, 105b and the self-lubricating rider ring 106 (hereinafter referred to as ring body) come in contact with the cylinder, and thereby smooth slidability between the piston and the cylinder can be secured. In such a fluid machine, since the cylinder is made of a metal material harder than the piston ring, the ring body is abraded by the sliding contact, and when the abrasion exceeds the limit by the long run, the outer circumference (the land section) of the piston comes directly and slidably in contact with the cylinder, and sometimes drag or the like takes place. Particularly, in the case of a compressor whose compression ratio is 5 bar or over, since a compression heat of about 300 °C is applied to the upper surface of the piston at the time of the maximum compression, thermal expansion occurs, resulting in a problem that even small abrasion of the ring body causes the piston to come slidably in contact with the cylinder. To overcome such a defect, in the known compressor, a polytetrafluoroethylene (PTFE) type resin material good in sliding performance is used for the ring body, and the clearance between the piston and the cylinder is set in the order of 1 to 2 % (0.5 to 1 mm for a piston outer diameter of 50 mm ⊘) for the piston outer diameter. However, in such a constitution, the clearance between the piston and the cylinder becomes unnecessarily excessive, for example, in the early stage of the compression, or in the intermittent operation, and correspondingly the compression efficiency is liable to lower. To overcome the defect, a technique is disclosed wherein the surface of the piston made of aluminum material is coated with a self-lubricating resin, and even if the piston outer circumference is allowed to come directly and slidably in contact with the cylinder, drag or the like is prevented from taking place, but since the heat resistance strength of the self-lubricating resin such as PTFE often used in conventional piston rings or the like is about 200 to 250 °C, if the adiabatic compression ratio is brought to 5 bar or over, the compression heat easily reaches the heat resistance temperature of the PTFE or higher, leading, for example, to a possibility of deterioration, or deformation of the piston surface coating, or a possibility of occurrence of peeling or cracks of the piston surface coating caused by the difference in coefficient of thermal expansion between the piston body made of aluminum material and the piston surface coating. Therefore, this technique is accompanied by a defect that the technique cannot be applied except compressors for low pressure wherein the temperature rise due to the compression heat is low. Further, in any of the above prior techniques, although the piston itself is made of a metal material, particularly aluminum material in order to make it light in weight, since aluminum material is high in coefficient of thermal conductivity, the compression heat received at the piston top surface is transmitted to the whole piston, and particularly the temperature of the pinhole section for transmitting the movement of the connecting rod for driving the piston through the piston pin becomes high. In addition in the case of an oilless compressor, since means of cooling said piston pin section with an oil cannot be used, heat resistant bearing parts or the like must be used, the load on the piston pin section is large per unit area in comparison with other bearing, and as a result a bearing having heat resistance and load bearing quality must be used, which makes the cost higher and leads to liability of lowering the durability. Taking the defects of the prior art into consideration, an object of the invention is to provide an oilless reciprocating compressor/expansion apparatus wherein drag or lowering of the compression efficiency (expansion efficiency) will not take place. Another object of the present invention is to provide an oil less reciprocating compressor wherein if high compression heat comes in contact with the piston top, deformation, deterioration or the like of the piston will not take place. These objects are met by the invention as set out in claim 1. Preferred embodiments of the invention are set out in the dependent claims. The thermosetting condensed polycyclic polynuclear aromatic resin (COPNA resin) is described in detail in US-A-4,758,653. The COPNA resin has a plurality of condensed polynuclear aromatic hydrocarbon nuclei crosslinked by aromatic nuclei through methylene linkages. The crosslinked resin is obtained by thermosetting a composition, which comprises a raw material containing one or more condensed polynuclear aromatic compounds having at least three condensed benzene rings, a crosslinking agent containing an aromatic compound having at least two hydroxymethyl or halomethyl groups and an acid catalyst in specific amounts as set out in the above cited US patent. The crosslinking may be performed in one step or in two steps via an intermediate condensation product (B stage resin). According to the above-mentioned embodiment of this invention, since the heat deformation temperature of the COPNA resin itself is 250 °C or over, and the molding resin further containing graphite or the like that is a material high in heat resistance is molded, the heat resistance can easily be retained at about 300 °C or over, and therefore if the adiabatic compression ratio is set at 5 bar or over (the compression heat being about 300 °C), the piston is not deformed thermally at all and the heat resistance would not be deteriorated for a long time of period. Further, since said composite material is mixed with graphite or the like to increase the slidability and is molded, the composite material has a self-lubricating function, and as a result if the piston itself comes in slidably contact with the cylinder, smooth sliding performance can be obtained without dragging or the like. Further, since the coefficient of thermal expansion thereof is much lower than that of aluminum material, if the clearance between the piston and the cylinder is made small, problems will not occur, and the compression efficiency can be improved. In this case, the most preferable clearance to secure high compression efficiency without causing drag due to thermal expansion is to allow firm fitting to such an extent that will not cause drag, and more specifically the clearance is to be set preferably in the range of 0.1 to 5 % at normal temperatures for the diameter of the piston. Particularly, since said piston is low in coefficient of thermal expansion in comparison with that of aluminum material, the compression heat amount stored in the piston top is large, and the coefficients of thermal expansion at the upper part and the lower part of the piston are different during the compression operation, so that the clearance between the piston and the cylinder become ununiform, which is liable to affect adversely the compression efficiency. Consequently, in a preferred embodiment of the present invention, the diameter of the higher side of the piston is made smaller relatively to the diameter of the lower side, and preferably it is made thicker toward the end. On the other hand, the fact that said composite material is much lower in coefficient of thermal expansion in comparison with that of aluminum material rather brings about a preferable effect on the bearing section on the piston pin side. That is, according to the embodiment of claim 5, since the piston made of the composite material is low in coefficient of thermal expansion, the rate of the amount of the compression heat received by the piston top surface that is released from the metal cylinder is larger than the rate of the amount thereof that is transmitted to the piston side from said top, and as a result the rise in temperature of the piston pinhole is suppressed. Consequently, the piston pin section can be formed without taking heat resistance into consideration, and since said piston itself is provided with a self-lubricating function, the piston pin can directly be fitted without providing a specific bearing member. Thus, the number of parts can be reduced, the cost can be lowered, and since said pinhole section is not exposed to high temperatures, the durability can be improved. Said pinhole section undergoes an impact at the time of transition from the ascending step of the piston to the descending step or from the descending step to the ascending step. In the construction using a prior bearing, said impact brings about deterioration or the like of the bearing, while, in the present invention, since the piston made of a resilient composite material is allowed itself to function as a bearing, the piston absorbs the impact, and therefore the durability can be improved. Since the heat conduction of the piston itself of the abovementioned embodiment is low in comparison with that of aluminum material, the piston pin can be prevented from being heated too much, but high heat is accumulated in the piston top on the contrary, and therefore there is a possibility that the compression efficiency is lowered even through the temperature will not exceed the heat resistance temperature of the composite material itself. Thus, according to the embodiments of claims 6 to 8, the smooth sliding function of the cylinder and the piston pin section and the heat resistance (heat transmitting) function on the side of the top opposite to the discharge/suction valve, that is, the side of the piston top in contact with compression heat are separated, at least the part of the outer circumferential section that slides on the cylinder and the piston pinhole section are made of a self-lubricating heat-resistant material, and the piston top is made of a material good in heat conductivity such as aluminum, thereby overcoming the above defect. According to the above constitution, since the piston top side in contact with the compression heat is made of aluminum or the like, for example even if the adiabatic compression ratio is made high and the compression heat rises to about 300 °C, the top will not deformed or deteriorated, and said top will be cooled by the contact with the cool sucked gas. Thus, the compression heat is not accumulated and released easily through the discharged air, and as a result the temperature transmitted to the part made of the self-lubricating heat-resistant material located below it is not heated near to the compression heat, and if the self-lubricating material comprises for example a fluorocarbon resin whose heat resistance temperature is low, the temperature can be retained at or below the heat resistance temperature easily. In this case, by making, of a good heat conductor, the top land to which the compression temperature is easily transmitted as well as the piston top, said heat releasing efficiency can be further improved, and the use of a fluorocarbon resin low in heat resistance temperature becomes further possible, but in this case, by making the outer diameter of said top land section slightly smaller than the diameter of the piston below it in order to obviate the sliding on the cylinder side, drag of the top land section is prevented,and smooth piston sliding performance is secured. That is, at least the outer circumferential surface side of said piston body that slides on the cylinder is made of a self-lubricating material, and since said outer circumferential surface obviates the transmission of the compression heat as far as possible, smooth slidability can be secured even if a material low in heat resistance temperature is used. As stated in claim 7, the constitution of the invention is such that a piston is formed by integrally molding said composite material around a piston core made of a metal material, and more particularly the piston outer circumference that slides on the cylinder and said pinhole part may be integrally molded using a thick coating of said composite material with the piston top and the core of a metal material on the back side thereof exposed. Also, as stated in claim 8, the piston body is made of a self-lubricating heat-resistant material, a metal body good in heat conductivity is arranged at least on the piston top side opposite to the discharge valve, and they may be integrated by using an arbitrary fixing means. In this case, by extending the good heat conductor on the piston top side substantially to the back side of the piston top directly or through joining bodies such as rivets, the heat is released from the inside of the piston to reduce the movement of the heat to the piston sliding surface side, the increase of the temperature on the circumferential section side can be avoided as far as possible, and smooth slidability between the piston and the cylinder can be secured. Brief Description of the Drawings Fig. 1 is a cross-sectional view, showing an oilless reciprocating compressor to which the present invention is applied. Fig. 2 is a cross-sectional view, showing the constitution of essential parts of an oilless reciprocating compressor according to an embodiment of the first invention. Fig. 3 is a cross-sectional view, showing the constitution of essential parts of a prior art oilless reciprocating compressor. Figs. 4, 5, and 6 are cross-sectional views, respectively showing pistons of embodiments of the second invention. Fig. 7 shows a piston of another embodiment, and (a) is a view thereof, partly in cross section, and (b) is a bottom plan view thereof and a cross-sectional view taken along line A-A'. Now, preferable embodiments of the present invention will be illustrated in detail with reference to the drawings. However, unless otherwise specified, the dimensions, materials, shapes, relative positions, etc. of the constitutional parts of the illustrated embodiments are not intended to limit the scope of the invention, but are described for the purpose of illustration. Now, referring to Fig. 1, the essential parts of the constitution of an oilless compressor to which the present invention is applied will be described. Reference numerals 2 and 3 indicate respectively a cylinder and a cylinder head made of aluminum or other metal material good in electroconductivity, and a spacer 4 in which a discharge valve 4A and a suction valve 48 are built is sandwiched between the members 1 and 2. The inside of the cylinder head 3 is divided by a partition wall 3A into cells, one of which is provided with a suction port 3B in communication with the suction valve 4B and the other of which is provided with a discharge port 3C in communication with the discharge valve 4A. On the other hand, a piston 1 around which a piston ring 5 is fitted is fitted in the cylinder 2, and can be reciprocated through a connecting rod 6 and a piston pin 7 by the rotation of a crank-shaft 8 in known manner, so that the air sucked into the space over the top of the piston 1 via said suction valve 4B is adiabatically compressed can be discharged from the discharge valve 4A toward the discharge port 3C to perform the prescribed compression operation. Since this operation is well known, the description is omitted. Fig. 2 shows a first embodiment of the invention, showing the constitution of essential parts of the piston and the cylinder section to be built in the above oilless compressor. The cylinder 2 is made of an aluminum alloy as known in the art, the outer circumferential surface is provided with fins 2a, and the piston sliding section on the inner circumferential side is treated to have a hard anodizing film. Before describing the shape of the piston 1, the procedure of the production of the piston 1 will be described in detail. The piston 1 is molded using a molding material, which as she in US-A-4,758,653, is prepared by mixing a resin material (available under the trade name of SK resin (SUMITOMO METALS CO., LTD.,) and described in the firm's brochure SK-RESIN of Sumitomo Metal Ind. of July 1989) based on a COPNA resin formed by crosslinking molecules of a condensed polycyclic aromatic compound through benzene rings each having two methylene chains in the parapositions (Japanese Patent Laid-Open (KOKAI KOHO) No. 521,522/1987) with graphite powder in a ratio of 6 to 4 under such molding conditions that the molding temperature is 170 to 220 °C, the molding pressure is 200 to 300 bar and the hardening time is 1 min per a thickness of 1 mm by the same compression molding means as for the molding of phenol resins. The thus formed piston 1 has the following physical properties: the coefficient of thermal expansion is 4.4 x 10⁻⁵/deg, and the coefficient of thermal conductivity is 4.69 kJ /m/.hr °C. The coefficient of thermal expansion and the coefficient of thermal conductivity of the thus formed piston 1 were 1.9 times and 86 times respectively as high as those of a conventional piston 1 made of a prior aluminum alloy (the coefficient of thermal expansion is 2.3 x 10⁻⁵/deg, and the coefficient of thermal conductivity is 0.054 kJ/m/.hr °C), indicating high heat-insulating properties and heat storing properties. Next, the shape of the piston 1 will be described. The outer diameter is increased from the piston top 13 toward the piston skirt section by taking the heat gradient into consideration, and since the difference Δb between the coefficients of thermal expansion of the piston 1 and the cylinder 2 is 2.1 x 10⁻⁵/deg, assuming the difference between temperatures of the upper part and the lower part of the piston 1 to be Δt, and the outer diameter of the piston 1 to be P, if the difference of the diameter is set as Δt.P (2.1 x 10⁻⁵/deg), the clearance of the piston 1 and the cylinder 2 at the compression operation can be kept uniform. Since the compression heat received at the piston top 13 is about 300 °C, by setting said clearance to be about 0.1 to 0.5 % at normal temperatures for the diameter of the piston 1, dragging would not take place during the compression operation, and the clearance between the piston 1 and the cylinder 2 can be made to be a minimum value that will not impede the reciprocative movement, then since the whole of the outer circumference of the piston 1 can be caused to function as a surface sliding on the surface of the cylinder 2, the graphite of the piston is transferred to the cylinder thereby improving the slidability and sealing properties, and thus leakage of the gas that will occur through the circumferential surface of the piston, from the opening section of the below-mentioned piston ring 5, etc. can be reduced thereby improving the compression efficiency. The piston 1 is formed with a ring groove 11 and a pinhole 12 below the ring groove 11. The ring groove 11 is in the form of a ring and is located near the piston top 13. The piston ring 5 made of PTFE resin is fitted in the ring groove 11. In this embodiment, since the piston itself is provided with a sealing effect to a certain degree, it is not required to provide two piston rings 5 as in the prior apparatus, and the single piston ring 5 can secure a prescribed sealing effect. Said pinhole 12 is extended through approximately the middle position of said piston 1, and is abraded so that it may function directly as a bearing. A piston pin 7 is applied to said pinhole 12, and the piston 1 is moved up and down by the rotational movement of the crankshaft through the connecting rod 6. In this case, at the transition from the ascending step of the piston 1 to the descending step or the transition from the descending step to the ascending step, the piston 1 undergoes a shock, and in the structure using a prior bearing, deterioration and the like of the bearing would occur due to the shock, but in the present invention since the resilient piston 1 itself is allowed to function as a bearing, the shock is absorbed by the piston 1, and therefore the durability can be improved. When a prior piston 101 shown in Fig. 3 was used in the above-mentioned oilless compressor, and the piston of this embodiment was used in the above-mentioned oilless compressor (the piston diameter: 50 mm), and after they were operated continuously under a load of 7 bar for 1,000 hours, they were disassembled. As a result, a dragged mark was observed at the land section of the piston of the prior compressor, and it was confirmed that the bearing fitted to the pinhole 12 of the piston pin 7 worn out, causing the noise during the operation under the load to become large. On the other hand, after the passage of 1,000 hours, although the one of this embodiment had an accustomed mark on the sliding surface, it had not a dragged mark, the degree of the wear at the pinhole 12 was very little, and it was confirmed that there was not looseness between the pinhole 12 and the piston pin 7. With respect to the temperature, a decrease of 25 °C can be observed at the piston section. Fig. 4 shows a piston of a second embodiment of the invention used in the above compressor, and the piston 10 is formed by integrally molding a thick coating of said composite material 10B around the a piston core 10A made of a metal material. The specific constitution will be briefly described. Said piston core 10A is made of an aluminum alloy, the upper surface is made flat, and the inner circumferential surface side is provided with a finlike projection 14 along the axial direction. The thick coating of said composite material 10B is integrally molded with the outer circumference of the piston core 10A and the piston pinhole 12 to form the Piston 10. That is, with the piston top 13 and the piston core 10A on the back side thereof exposed, the thick coating of said composite material 10B surrounds the outer circumference of the piston 10 in slidably contact with the cylinder 2 and said pinhole 12. Preferably, the thickness of said composite material 10B is 1 to 3 mm on the pinhole 12, and about 2 to 3 mm on the circumferential section in the case of the piston 10 having a diameter of 50 ⊘. According to this embodiment, the same effect as that of the first embodiment can be obtained, and since the piston top 13 and the inner circumferential side whose temperature will become the highest are made of an aluminum alloy good in heat conductivity, the compression heat generated at the piston top 13 is radiated through the inner circumferential surface of the piston 10, it can be used thus in a high-pressure compressor, and therefore the compression efficiency can be improved. For example, with respect to the rise in the temperature of the embodiment 1 shown in Fig. 2 wherein the whole of the piston 1 is made of a composite material and the rise in the temperature of the piston 10 of this embodiment after the operation for 1 hour under a load of 7 bar, in the embodiment 1, the rise in the temperature at the back of the piston 1 was 125 to 130 °C, while in this embodiment the rise of the temperature was 80 to 90 °C, which is a great decrease, and at the piston pinhole 12 the decrease in the temperature was about 10 °C lower than that of the embodiment 1, so that it could be estimated that the durability would be improved. Fig. 5 shows a modification of the above embodiment, illustrating a piston wherein all of the outer circumferential section of the piston 20 is made of said heat resistant composite material 20 B, a head section 20A Surrounded by the piston is made of an aluminum alloy, and a plurality of depending radiation fins 21 are provided on the inner circumferential surface side of the head section 20A, and according to the embodiment, in addition to the effect of the above-mentioned embodiment, the heat dissipation of the piston top 13 is increased by the radiation fins 21 so that the cooling effect of the piston 20 is further increased, and since all of the outer circumferential section 20B is made of a self-lubricating heat-resistant composite material, its sliding on the cylinder is completely cut off. In the above-mentioned second embodiment, since there is a resin material 20B of a top land section that receives the compression heat directly, there is no way other than to use, as the resin material, a highly heat resistant COPNA resin composite material. Therefore, to overcome the above defect, in Fig. 6, the top land 14 and the piston top 13 over the ring groove 11 comprise a piston head 30A made of aluminum material and having a prescribed thickness and a piston body 308 of a self-lubricating heat-resistant material integrally molded with the head 30A to form a piston 30 The head 30A including the top land 14 and the piston top 13 having prescribed thicknesses and located over the ring groove 11 is made of aluminum material, and the piston body 308 including the ring groove 11 located below it is integrally molded. In the head 30A, the outer diameter of the top land 14 is made slightly smaller than the diameter of the piston body 30B below it, and its lower side 31 is bent in the shape of the letter L in cross section to facilitate the association with the piston body 30B. The piston body 30B may be formed by using a molding material of SK resin with which 40 % of graphite are mixed similarly to the above-mentioned embodiment, and casting and molding said molding material integrally with said head 30A previously molded and cured, or may be made of PTFE resin or its composite material similarly to the piston ring 5 since the heat on the side of the piston top 13 does not come in direct contact with the resin body. According to this embodiment, Since the head 30A that is good in heat conductivity comprises the piston top 13 as well as the top land 14 to which the compression heat is liable to be most transmitted, the heat dissipation effect is further improved, and since said material is used on the side of the piston body, it becomes Possible to form a good piston whose heat resistance temperature is 300 °C or over, which means that it will be less deformed thermally. Fig. 7 shows another embodiment of a piston 40 using a joining means by rivets, wherein a piston body 40B and a head 40A are separately formed, and then are integrally fixed by rivets 41. That is, the head 40A is in the shape of the disk that will be formed by cutting the piston 40 horizontally over the ring groove 11, the diameter thereof is made slightly smaller than the diameter of the piston body 40B located below it and made of a self-lubricating resin material, and as shown in Fig. 7 (b) said head 40A and the piston body 40B are fixed integrally by four rivets 41 good in heat conductivity, and the rivet ends 41a are extended to the back of the piston top 13. Thus, the compression heat transmitted toward the head 40A can be released below the piston through the rivets 41 or can be diffused throughout the piston body 40B, and if the head 40A is made thinner, the embodiment can have the same effect as that of the above-mentioned embodiment, and the head 40A and the body are fixed by the rivets 41 good in heat conductivity while the rivet ends 41a are extended to the back of the piston top 13. Thus, the compression heat transmitted toward the head 40A can be released below the the piston through the rivets 41 or can be diffused throughout the piston body 40B, and therefore if the head 40A is made thinner, the thermal disadvantage can be obviated.

Claims: An oil-less reciprocating compressor/expansion apparatus, comprising a piston body (1, 10, 20, 30, 40) to which a piston ring (5) made of a self-lubricating material is fitted, said piston having a pinhole section (12) for attachment of a connecting rod (6), characterized in that at least the part of the piston body (10B, 20B, 30B, 40B) in slidable contact with the cylinder (2) and the pinhole section (12) are made of a self-lubricating composite material containing a thermosetting condensed polycyclic polynuclear aromatic resin, and graphite or other heat-resistant material for increasing slidability. The apparatus of claim 1, wherein a piston pin (7) is directly journaled in said pinhole (12) extended through the barrel section of said piston body (1) without a bearing. The apparatus of claim 1 or 2, wherein the clearance between the piston body (1) and the cylinder (2) at least near the piston top (13) is set in the range of 0.1 to 0.5 % of the piston diameter at normal temperature. The apparatus of any one of claims 1 to 3, wherein the diameter of the upper side of the piston body (1) is smaller than that of the lower side. The apparatus of claim 1, wherein the complete piston body (1) is made of said self-lubricating composite material containing a thermosetting condensed polycyclic polynuclear aromatic resin, and graphite or other heat-resistant material for increasing slidability. The apparatus of claim 1, wherein a top land section (14) at the circumference above the first piston ring (5) as well as the piston top (13) is made of a material good in heat conductivity, and the outer diameter of the top land section (14) is slightly smaller than the diameter of the piston (30) below it. The apparatus of claim 1, wherein a self-lubricating composite material (10B) containing a thermosetting condensed polycyclic polynuclear aromatic resin, and graphite or other heat-resistant material for increasing slidability is integrally molded around a piston core (10A) made of a material good in heat conductivity to form the piston (10). The apparatus of claim 1, wherein said piston (40) comprises a piston body (40B) made of a self-lubricating composite material containing a thermosetting condensed polycyclic polynuclear aromatic resin, and graphite or other heat-resistant material for increasing slidability, to which a piston head (40A) made of material good in heat conductivity is attached by fixing means (41). The apparatus of claim 8, wherein said fixing means (41) are rivets. The apparatus of any one of claims 6 to 8, wherein said material good in heat conductivity is a metal material, preferably an aluminum alloy.

Inventors: IIDA TOSHIO, IIDA, TOSHIO
Applicants: IWATA AIR COMPRESSOR MFG, IWATA AIR COMPRESSOR MFG. CO.,LTD.
Application year: 1990
Main classification: F04B39
IPC codes: F04B39, F16J1, F16J9