Reciprocating compressor

Information

  • Patent Grant
  • 6589024
  • Patent Number
    6,589,024
  • Date Filed
    Friday, July 27, 2001
    23 years ago
  • Date Issued
    Tuesday, July 8, 2003
    21 years ago
Abstract
A reciprocating compressor provided with a plurality of gas compression means having a cylinder and a piston, the piston of each gas compression means is cooperated with the, compressor by converting a rotating motion of a crankshaft provided on an electric drive source to a reciprocating motion by a scotch yoke mechanism, wherein an increase of the volume of discharged gas can be achieved without designing a gas compression means to be wide or without increasing the number thereof, a pulsation of discharged gas can be decreased by an attachment of an expression muffler on the cylinder head so as to decrease a vibration and noise of the compressor, an attachment of the fly wheel to the crankshaft and an adjustment of the shaft with the crankshaft can be improved easily, further compressed gas flows are joined and discharged in concentration, thereby the pulsation of discharged gas can be restrained.
Description




BACKGROUND OF THE INVENTION




1. Field of the Invention




The present invention relates to a reciprocating compressor in which a plurality of gas compression means having a cylinder and a piston is provided, the pistons of each gas compression means are formed to cooperate by converting a rotating motion of a crankshaft provided on a driving source to a reciprocating motion.




2. Detailed Description of the Prior Art




In a normal reciprocating compressor, one gas compression means having a cylinder and a piston is provided, while there has been a reciprocating compressor having a plurality of gas compression means conventionally. In such reciprocating compressor having a plurality of gas compression means, for embodiment as shown by FIG.


9


(


a


), three gas compression means


101


,


102


,


103


having the cylinders and the pistons are oppositely arranged to achieve a reciprocating motion of the piston on orthogonal axis


105


,


106


, it is known that gas is compressed and high-pressurized from the gas compression means


101


in turns and that the gas compression means


103


is designed to be a final stage high pressure compression means.




In the reciprocating compressor


100


, a pair of opposite pistons


51


,


53


is connected to a yoke


1


A, the other pair of opposite pistons


52


,


54


is connected to a yoke


1


B of which phase is shifted to an angle of 90 degrees. The compressor having a scotch yoke mechanism that a crankshaft


57


is rotated by a rotor


56


of an electric drive mechanism


55


as shown by FIG.


9


(


b


), a crank pin


58


is eccentrically rotated around the crankshaft


57


, a pair of pistons


51


,


53


is reciprocated only in the direction of an axis


105


and the other pair of pistons


52


,


54


is reciprocated in only the direction of the axis


106


.




As shown by

FIG. 11

as a model, the scotch yoke mechanism is a kind of double slide crank mechanism to convert the rotating motion to the reciprocating motion or to do the reciprocating motion to the rotating motion. In this case the rotating motion is converted to the reciprocating motion, in the scotch yoke mechanism having the yokes


1


A,


1


B, a crank pin


58


is attached between a lower balancer


59


and an upper balancer


60


which are mounted on a crankshaft


57


as shown by FIG.


10


and is engaged with yokes


1


A,


1


B, thereby the vibration or the like of the compressor is controlled and the compression can be operated in stable.




In the reciprocating compressor


100


described hereinbefore, it is described herein that in accordance with an increase of compression stages, diameters of the cylinder and the piston of the gas compression means toward the high pressure side are designed to be smaller and each compression means is engaged and, cooperated with the crank pin so as to actuate in a process of shifting its phase to a determined angle.




SUMMARY OF THE INVENTION




In the conventional reciprocating compressors, the compressed gas are highly pressurized one after another to achieve a predetermined gas pressure, however due to less inner volume of each gas compression means toward the high pressure side, the volume of the final discharged compression gas is decreased. In accordance with an object, for embodiment, for using the compressor for a gas supply stand for natural gas vehicles, a gas injection molding machine, an electric insulating gas (6-sulfur fluoride) collecting device, carbon dioxide coolant and refrigerating cycle and the like, especially it is requested to supply a large volume of compressed gas. To correspond with these requirement, the inner volume thereof can be increased by providing a large diameter of the cylinder and the piston of the compression means, however it will cause a large sizing of the compressor, an increase of electric consumption of the electric drive portion and a high cast. Further to use a plurality of compressors will cause an increase of space where compressors are located and an increase of the cost and the like.




It is the first object of the present invention that in a reciprocating compressor having a plurality of gas compression means, the volume of discharged gas can be increased without using a plurality of compressors.




Further in the conventional reciprocating compressor, the pulsation is caused by a discharged gas around the discharge port of each gas compression means


101


,


102


,


103


to make a vibration or a noise of the compressor. Therefore in conventional compressor, a muffler tube (not shown) is attached to the connecting tube with each gas compression means


101


,


102


,


103


to decrease the pulsation of discharged gas. However it is necessary to cut and remove a part of the connecting tube for mounting the muffler tube and to weld the muffler tube thereto, the troublesome working is caused, further the main body of the compressor is large-sized due to a larger diameter of the muffler tube than the outer diameter of the connecting tube and it has caused an increase of the cost due to an increase of manufacturing processes and of parts. The conventional muffler tube is inferior in its durability and has a problem of easily damaged by a high pressurized discharging gas.




It is the second object of the present invention to provide a reciprocating compressor to which the muffler is easily attached, which is designed in compact, in which a decrease of the cost of manufacturing and an improvement of its durability can be achieved.




Further in the conventional reciprocating compressors, in order to achieve a constant rotating speed of the crankshaft and to provide an stationary torque thereof, a flywheel is mounted on the lower end portion of the crankshaft. For attaching the flywheel, conventionally, for embodiment as shown in

FIG. 6

, a shaft hole


61




a


of the fly wheel


61


is shrinkage fit to the lower end portion of the crankshaft


57


which is projected from the shaft hole of the rotor


56


. While an external thread is provided at the lower end portion of the crankshaft


57


and the internal thread is provided at the shaft hole of the flywheel


61


to be engaged with each other for receiving the flywheel. In accordance with conventional means for attaching flywheel, the attachment work is troublesome, further it is difficult to adjust respective axis of the crankshaft


57


and of the flywheel


61


, and a slight movement will be caused since an axial line of the flywheel


61


is incliningly attached.




It is the third object of the present invention to provide the reciprocating compressor improved in easy attachment work of the flywheel and in an easy adjustment with the crankshaft to prevent the shaft from shifting.




Furthermore in the conventional reciprocating compressor, in order to increase the volume of discharged gas, gas compressed in a plurality of gas compression means are joined at the one place by connecting tube and are discharged in concentration. In this case, the compression performance of each gas compression means is set to be identical by designing the cylinder and the piston to be same size, the compression action of each gas compression means is shifted with a certain intervals in accordance with a rotation of the crank pin, for embodiment, the compressor is so comprised that compressed gas flow is joined by connecting tubes to cylinder head which is provided in one gas compression means and the compressed gas is discharged in concentration from the cylinder head. However in such concentrate discharging type compressor, since compressed gas flows are joined via a plurality of connecting tubes into the cylinder head to interfere with each other, a large pulsation is caused. Therefore, the muffler is provided in each connecting tube to decrease the pulsation of discharged gas from each gas compression means, however it is troublesome to attach the muffler, moreover the increase of the cost due to large number of parts has been caused and there has been a problem of large sized main body of the compressor and the like.




It is the fourth object of the present invention to provide the reciprocating compressor of the type improved in decreasing the pulsation due to interference of the compressed gas flows which are joined without attaching the muffler in the connecting tube.











BRIEF DESCRIPTION OF THE DRAWINGS





FIG. 1



a


illustrates a plane view of an embodiment of a reciprocating compressor according to the present invention;





FIG. 1



b


is a partially cut-away front view of an embodiment of a reciprocating compressor according to the present invention;





FIG. 1



c


is a partially cut-away side view of an embodiment of a reciprocating compressor according to the present invention





FIG. 2

is a plane view of an embodiment of the reciprocating compressor according to the present invention is applied for an one stage compressor with two cylinders;





FIG. 3

is a plane view of an embodiment of the reciprocating compressor according to the present invention is applied for a two staged compressor mechanism with two systems;





FIG. 4

is a schematic cut-away view of an embodiment of an expansion muffler is attached to a cylinder head of a gas compression means;





FIG. 5

is a schematic cut-away view of a main portion illustrating for attaching a fly wheel to a crankshaft;





FIG. 6

is a schematic cut-away view of a main portion illustrating for attaching a conventional fly wheel to a crankshaft;





FIG. 7

is an explanation view imitating a reciprocating compressor according to the present invention;





FIG. 8

is an explanation view illustrating a condition of a gas compression wave fed via a connecting tube from each gas compressor;





FIG. 9



a


illustrates a horizontal cut-away view of a conventional reciprocating compressor;





FIG. 9



b


is a vertical front view of a conventional reciprocating compressor;





FIG. 10

is an explanation view of a crankshaft portion; and





FIG. 11

is an explanation view of a scotch yoke mechanism.











DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT




The embodiment of the reciprocating compressor in accordance with the present invention will be described with reference to accompanied drawings.




Embodiment 1




It is an embodiment to achieve the first object of the present invention in, FIG.


1


(


a


) illustrates a general of the reciprocating compressor by respective plane view, (


b


) is partially cut-away front view and (


c


) is partially cut-away side view. In a reciprocating compressor P


1


, four gas compressors that is, the first gas compression means


1


, the second one


2


, the third one


3


and the fourth one


4


are oppositely disposed one another in a cross shape. These four gas compression means


1


to


4


respectively include cylinders and pistons. These are different from the conventional reciprocating compressor described hereinbefore and these have one another the same inner volume and the same compressing performance. The piston of the first gas compression means


1


and the piston of the third gas compression means


3


are connected on the same axis with each other to one of yokes and the piston of the second gas compression means


2


and the piston of the fourth gas compression means


4


are connected on the same axis with each other to the other yoke of which phase is shifted to an angle of 90 degrees.




A cylinder head


5


is attached on a head portion of the cylinder in the fourth gas compression means


4


, a gas passage is provided in an interior thereof and a discharge port


5




a


is provided at the one end thereof. The discharge port la of the first gas compression means


1


, the discharge port


2




a


of the second gas compression means


2


and the discharge port


3




a


of the third gas compression means


3


are respectively connected to the gas passage by a first connecting tube


6


, a second connecting tube


7


and a third connecting tube


8


. Thereby the flow of gas compressed by each gas compression means


1


to


4


is joined to the gas passage of the cylinder head


5


.




The reciprocating compressor P


1


is un-lubricating type and includes a cooling device Q for cooling, as shown by FIG.


1


(


b


)(


c


), in which a fan motor


11


is mounted on a unit base


10


in a fan casing


9


, a cooling fan


12


is attached on an end of the rotating shaft of the motor and an air inlet


13


provided with a net is mounted on a side surface portion of the fan casing


9


. The reciprocating compressor P


1


is attached on the cooling device Q via a leg member


14


of which upper end is intervened with a rubber vibration isolator


15


so as to absorb the vibration of the compressor P


1


. Further on four corners in the casing


9


, supports


16


are stood for supporting the reciprocating compressor P


1


in stable. Numeral


17


illustrates a casing for cooling arranged on the periphery of the reciprocating compressor P


1


.


18


is a terminal cover for protecting a connecting terminal of an electric motor part


19


of the compressor P


1


.




In the reciprocating compressor P


1


designed as described hereinbefore, gas is supplied from a gas supply source (not shown) to an inlet port


20


which is mounted on an upper portion thereof and thereafter flows into cylinders of the first to the fourth gas compressing means


1


to


4


so as to be compressed by pistons. The compression process by the piston is achieved that a crank pin is rotated via the crank shaft in accordance with a rotation of a rotor of the electric motor part


19


to actuate two yokes of which phase is shifted to an angle of 90 degrees. For one rotation of the crank pin, the same as conventional ones, the first gas compression means


1


to the fourth gas compression means


4


are compressed in turns so that gas compressed by the first gas compression means


1


is discharged from the discharge port la and is fed into the cylinder head


5


via the first connecting tube


6


, in the same way as that, gas compressed in the second and the third gas compression means are fed into the cylinder head


5


respectively via the second and the third connecting tubes


8


. Further gas compressed by the fourth gas compression means


4


is fed from the discharge port


4




a


into the cylinder head


5


. Therefore gas flows respectively compressed in the first gas compression means


1


to the fourth gas compression means


4


are joined in the gas passage in the cylinder head


5


and are discharged in concentration from the discharge port


5




a


of the cylinder head


5


. Thereby a volume of compressed gas from the reciprocating compressor P


1


is increased to four times.




As described hereinbefore, the piston of the first gas compression means


1


and the opposite piston of the third gas compression means


3


are directly connected to one of yokes so that the gas suction via the third gas compression means


3


into the cylinder is achieved simultaneously with gas compression action by the first gas compression means


1


, to the contrary, gas compression action in the third gas compression means


3


is achieved simultaneously with gas suction via the first gas compression means


1


into the cylinder. In the same way, the piston of the second gas compression means


2


and the opposite piston of the fourth gas compression means


4


are directly connected to the other yoke of which phase is shifted to an angle of 90□degrees so that the gas suction via the fourth gas compression means


4


into the cylinder is achieved simultaneously with gas compression action by the second gas compression means


2


, to the contrary, gas compression action by the fourth gas compression means


4


is achieved simultaneously with gas suction via the second gas compression means


2


into the cylinder. Thereby in accordance with a rotation of the crank pin the compression action is repeated by the first gas compression means to the fourth gas compression means in turn, and a volume of compressed gas of which the flow is joined in the cylinder head


5


can be discharged continuously.




An embodiment of a single stage compression with four cylinders is described hereinbefore and as shown by

FIG. 2

, it can be achieved by a reciprocating compressor P


2


comprising a single stage compression with two cylinders so that the first gas compression means


21


and the second gas compression means


22


are oppositely disposed to have a composition that a discharge port


21




a


of the first gas compression means


21


and a cylinder head


23


at the side of the second gas compression means


22


are connected each other by a connecting tube


24


. In the reciprocating compressor P


2


, the flow of gas compressed in the first gas compression means


21


is fed into the cylinder head


23


via the connecting tube


24


and joined with gas compressed by the second gas compression means


22


and is discharged in concentration from a discharge port


23




a


of the cylinder head


23


. Thereby the volume of discharged gas can be increased two times.




In this case, a piston of the first gas compression means


21


and the piston of the second gas compression means


22


are connected to one yoke and reciprocated by the scotch yoke mechanism so that the gas compression is achieved at one side and the gas suction is achieved at the other side. Moreover it is not shown by drawings, a gas compression can be achieved by three cylinders or by five cylinders respectively arranged in facing with each other such as a star shape and the like other than a cross shape.




An embodiment of the compressor applied for two stage compression system is shown in

FIG. 3

, a reciprocating compressor P


3


comprises two stage compression mechanism with two systems in which four gas compression means are arranged in facing with each other in a cross shape. The first stage gas compression means


31


A,


31


B are arranged in shifting its phase to an angle of 90 degrees, the second gas compression means


32


A,


32


B are also arranged in shifting its phase to an angle of 90 degrees and the first stage gas compression means


31


A and the second stage gas compression stage


32


A are connected with each other by a connecting tube


33


B, thereby two stage compression mechanism RA, RB having two systems are formed so that discharge tubes


34


A,


34


B of second stage gas compression means


32


A,


32


B are joined at a point S to discharge gas in concentration.




The first stage gas compression means


31


A in the two stage compression mechanism RA and the second stage gas compression means


32


B in two stage compression mechanism RB are directly connected in an opposite position to one of yokes and the first stage gas compression means


31




b


of the two stage compression mechanism RB and the second stage gas compression means


32


A in the two stage compression mechanism RA are connected at an opposite position to the other yoke of which phase is shifted to an angle of 90 degrees. In this case, according to one rotation of the crank pin, gases are compressed by the first stage gas compression means


31


B,


31


A to the second stage gas compression means


32


A,


32


B in turn. Gases compressed by the first stage gas compression means


31


B,


31


A are fed into the second stage gas compression means


32


B,


32


A via the connecting tube


33


B,


33


A and are joined at the point S to discharge in concentration by discharge tube


34


B,


34


A. Thereby high pressurized gases respectively compressed by two stage compression mechanism RA, RB having two systems are joined and the volume of discharged gas can be increased two times.




In accordance with the present invention, in the reciprocating compressor having a plurality of gas compression means, the flows of gas compressed by each gas compression means are joined into an one place and are discharged in concentration, thereby it is not necessary to design the main body of the compressor in a large size or to use a plurality of compressors for increasing the volume of gas discharged in several times in accordance with numbers of gas compression means. Further two stage compression mechanism having two systems can be achieved and the volume of gas discharged can be increased by joining a high pressurized gas which is compressed in each two stage compression mechanism at one place and discharging it.




Embodiment 2




The second object of the present invention can be achieved by this embodiment, in

FIG. 4

, numeral


121


illustrates a discharge block which is mounted on a discharge port


5




a


of the cylinder head


5


in the fourth gas compression means


4


by a fastening bolt


122


. An expansion muffler


123


is formed at the joining portion for the discharge port


5




a


of the discharge block


121


. The expansion muffler


123


is formed by providing a space portion S having a larger inner diameter than that of the discharge port


5




a


of the cylinder head


5


and a discharge opening


124


having a smaller inner diameter than that of the space portion S is formed at the end of the muffler


123


. A gas supply tube (not shown) is connected to the discharge opening


124


.




As described hereinbefore, gases compressed by the first gas compression means


1


to the third gas compression means


3


are respectively fed into the cylinder head


5


at the side of the fourth gas compression means


4


through the first connecting tube


1


to the third connecting tube


3


to join with gas compressed by the fourth gas compression means


4


and are discharged to the discharge block


121


from the discharge opening


5




a


of the cylinder head


5


. Due to the expansion muffler


123


formed on the discharge block


121


, high pressurized gas from the discharge opening of the cylinder head


5


is rapidly decreased its pressure at the time of passing through the means S. Therefore the pulsation can be decreased and the vibration or the noise can be restrained in accordance therewith.




The discharge block


121


does not need much means for attachment on the discharge port


5




a


of the cylinder head


5


so as to prevent the main body of the reciprocating compressor from being large size. Since the discharge block


121


is easily attached by the fastening bolt


122


and an easy attachment work of the conventional muffler tube can be achieved and the number of processes, parts thereof and a cost of manufacturing can be restrained. Furthermore the discharge block


121


has more excellent durability than the conventional muffler tube and can correspond with a high pressurized discharge gas.




In the embodiment described above, the discharge block


121


contained with the expansion muffler


123


is attached to the cylinder head


5


only in the fourth gas compression means


4


and can be also attached respectively on the discharge opening of the first gas compression means


1


to the third gas compression means


3


. Thereby the pulsation of the discharged gas can be decreased more.




In accordance with the present invention, in the reciprocating compressor including a plurality of gas compression means, the expansion muffler is attached on at least one discharge port of the gas compression means so that the pulsation of the discharged gas can be decreased to restrain the vibration and the noise and an easy assembling work, a compact design, a reduction of a cost for manufacturing compressor and an improvement of the durability can be achieved.




Embodiment 3




The embodiment refers to achieve the third object of the present invention, in

FIG. 5

, numeral


221


illustrates a flywheel of which upper end portion is provided with a cylindrical attachment portion


221




a


and of which axial direction is provided with an attachment hole


221




b


. The cylindrical attachment portion


221




a


is formed on a base of a shaft hole


222




a


of a rotor


222


in the electric motor part


19


, that is, an outer diameter of the attachment portion


221




a


is designed to correspond with an inner diameter of the shaft hole


222




a


of the rotor


222


. For attaching the flywheel


221


, the cylindrical attachment


221




a


is inserted into the shaft hole


222




a


of the rotor


222


so as to contact its upper end surface with the lower end surface of the crankshaft


223


and a fastening bolt


224


is inserted into the attachment hole


221




b


to be threaded and fastened in a screw hole


223




a


which is provided in an axial direction of the crankshaft


223


.




At the time of attaching the flywheel on the crankshaft, an axial line of the flywheel


221


and one of the crankshaft


223


is accorded with each other and with an axial line of the rotor


222


too when the cylindrical attachment portion


221




a


of the flywheel


221


is inserted into the shaft hole


222




a


of the rotor and the upper end surface thereof is contacted with the lower end surface of the crankshaft


223


. Since the crankshaft


223


is so attached to the rotor


222


that the axial line of the crankshaft


223


is previously accorded therewith, the axial line of the flywheel


221


is accorded with the crankshaft


223


via the rotor


222


. Thereby an adjustment of axial lines of the flywheel


221


and the crankshaft


223


can be achieved more easily than the conventional ones and since the flywheel can be fixed by not a shrinkage fit but one bolt so as to achieve a easy working. It is enough to provide the screw hole


223




a


at the side of the crankshaft


223


and less of the thread work can be achieved than a conventional screw type. In this case the connecting portion between the flywheel


221


and the crankshaft


223


is supported by the shaft hole


222




a


of the rotor


222


a so as to achieve a good stability.




Numeral


225


is a key to connect the cylindrical attachment portion


221




a


of the fly wheel


221


and the lower end portion of the crankshaft


223


. As described hereinbefore, the flywheel


221


can be easily inserted into the shaft hole


222




a


of the rotor


222


by adjusting respective key grooves (not shown) provided on the cylindrical attachment portion


221




a


and the crankshaft


223


. The key


225


has a function to reinforce the connection of the flywheel


221


and the crankshaft


223


and to prevent them from loosening. Thereby the good stability at the time of starting and stopping the compressor can be achieved.




In accordance with the present invention, the cylindrical attachment portion of the flywheel is formed on the base of the inner diameter of the rotor shaft hole in the reciprocating compressor and further the cylindrical attachment portion is inserted into the rotor shaft hole so as to adjust axial lines of the flywheel and the crankshaft, the flywheel can be threaded and fastened by one fastening bolt, thereby an easy attachment of the fly wheel can be achieved and excellent effects such that the axial adjustment with the crankshaft is easy with preventing the shaft from moving slightly and the like.




Embodiment 4




The embodiment refers to achieve the fourth object of the present invention, in

FIG. 7

, the reciprocating compressor P


1


is shown as a model so that the length of the first connecting tube


6


is shown by L


1


, the length of the second connecting tube


7


is shown by L


2


and the one of the third connecting tube


8


is shown by L


3


, further the direction (as referred the fourth connecting tube


4




b


) from the fourth gas compression means


4


to the cylinder head


5


is shown by L


4


. Each inner diameter of connecting tubes is designed in same size.




As described hereinbefore during one rotation of the crank pin, gas is compressed by the first gas compression means


1


to the fourth gas compression means


4


in turns and the flow of compressed gas is joined to the cylinder head


5


to be discharged in concentration. The pulsation of compressed gas can be restrained if pressure waves are competed with each other at the joining point T. Since first gas compression means to the fourth gas compression means are shifted respectively in their phase to an angle of 90 degrees (π/2), it is necessary for the pressure wave of each compressed gas arrived to oppose with each other for one rotation (2π) of the crank pin.




The length of each connecting tube in the reciprocating compressor P


1


is limited to a certain range due to a whole size of the compressor, for embodiment the preferable length L


2


of the second connecting tube


2


is set to 1.133 m within the range thereof. The wave form of compressed gas passing through the second connecting tube


2


is measured by a pressure sensor attached thereto, there are appeared five crests of wave forms during one rotation of the crank pin and the rotating speed of the crank pin is 1800 rpm. The length L


2


of the second connecting tube


2


is 1.133 m, further each preferable length of other connecting tubes within a range limited due to the whole size of the compressor is tested, then it is found that the pulsation is hold minimum by L


1


=0.708 m, L


3


=0.436 m, L


4


=0.298 m. After checking pressure wave forms of compressed gas passing through the first connecting tube


1


, the third connecting tube


3


and the fourth connecting tube


4


, during one rotation of the crank pin, there are


8


crests of wave form for the first connecting tube


1


,


13


crests of wave form for the third connecting tube


3


and


19


crests of wave form for the fourth connecting tube


4




b.






In accordance with these wave tops, each pressure wave of which phase is shifted to an angle of 90 degrees is shown by

FIG. 8

, at the time of one rotation (2π) of the crank pin, it is shown that each pressure wave of the first gas compression means


1


and the opposite third gas compression means


3


is opposed to each other and each pressure wave of the second gas compression means


2


and the opposite fourth gas compression means


4


is opposed to each other. These cycles are repeated so that gas is discharged in concentration from the joining point T to the cylinder head


5


and the pulsation can be restrained at that time.




In accordance with the present invention, in the reciprocating compressor having a plurality of gas compression means, the length of each connecting tube for discharging compressed gas from each gas compression means to the joining point of the cylinder head is set to a predetermined length, thereby the pulsation of gas discharged in concentration can be hold minimum. Thereby the vibration or the noise of the reciprocating compressor can be excellently decreased. Further it is not necessary to attach the muffler to each connecting tube as a conventional type, thereby it can be prevented from a troublesome attachment work, an increase of the cost due to large number of parts or a large size of a main body of the compressor.



Claims
  • 1. A reciprocating compressor provided with a plurality of gas compression means having a cylinder and a piston, wherein each of the gas compression means is oppositely disposed with respect to another of the gas compression means, in which the pistons of each gas compression means are cooperated with the compressor by converting a rotating motion of a crankshaft provided on an electric drive source to a reciprocating motion by a scotch yoke mechanism, characterized in that a sucked gas is compressed by each gas compression means, and the flows of compressed gases from each gas compression means are joined to one place so as to be discharged in concentration, wherein gases compressed by all but one of the gas compression means are respectively discharged into a cylinder head of like other remaining one of said the compression means by a connecting tube so as to be joined with gas compressed by the other remaining one of the gas compression means and discharged in concentration from a discharge port of the cylinder head of the other remaining one of the gas compression means.
  • 2. A reciprocating compressor according to claim 1, wherein four of the gas compression means are oppositely disposed in a cross shape.
  • 3. A reciprocating compressor according to claim 1, wherein two of the gas compression means are oppositely disposed, gas compressed by one of said gas compression means is discharged into a cylinder head of the other gas compression means by a connecting tube to join with gas compressed by said other gas compression means, and is discharged in concentration from the cylinder head thereof.
  • 4. A reciprocating compressor comprising four gas compression means which are arranged oppositely with each other in a cross shape, two stage compression mechanisms with two systems composed of the first stage gas compression means and the second stage compression means by these four gas compression means are formed, wherein the first stage gas compression means and the second stage gas compression means in each system are respectively connected by a connecting tube, gas compressed by the first stage gas compression means is discharged into the second stage gas compression means, and the flows of further gases, compressed by the second stage gas compression means in each system are joined at one place to be discharged in concentration, wherein gases compressed by all but one of the gas compression means in each system are discharged into a cylinder head of the other remaining one of said the compression means in the system by the respective connecting tube of the system so as to be joined with gas compressed by the other remaining one of the gas compression means in the system and discharged in concentration from a discharge port of the cylinder head of the other remaining one of the gas compression means in the system.
Priority Claims (4)
Number Date Country Kind
2000-228937 Jul 2000 JP
2000-228940 Jul 2000 JP
2000-228948 Jul 2000 JP
2000-228953 Jul 2000 JP
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4645428 Arregui et al. Feb 1987 A
5584675 Steurer et al. Dec 1996 A
5846059 Mizuno et al. Dec 1998 A