JP4041173B2 - Low vibration positive displacement machine - Google Patents

Description

[0001]
[Industrial application fields]
The present invention relates generally to positive displacement machines, and more particularly to a low vibration positive displacement machine such as a compressor for refrigeration and air conditioning or an internal combustion engine for driving a generator.
[0002]
[Prior art]
Unlike non-volumetric machines such as turbomachines, electric motors, and generators, positive displacement machines consume and generate power intermittently, so their drive torque and output torque fluctuate periodically. Excitation torque, which is a couple that periodically fluctuates, acts from the outer shell portion of the outer periphery of the outer periphery of the outer periphery of the outer shell, and is a source of vibration. In conventional positive displacement machines, measures against this vibration include the operation of multiple working chambers with different cylinders and different phases to reduce fluctuations in drive torque and output torque, and floating the mounting part with a spring. Measures have been taken to block vibration.
[0003]
[Problems to be solved by the invention]
With the above-mentioned conventional technology, the number of cylinders and vibration isolation are theoretically difficult to eliminate even if the vibration of the positive displacement machine can be reduced, completely eliminating the problems of discomfort caused by vibration and damage to surrounding parts. I couldn't do it. In addition, the above measures have a problem that the manufacturing cost increases due to the complicated structure and the increased number of parts.
[0004]
It is an object of the present invention to eliminate a vibration generated by a positive displacement machine consuming or generating power intermittently almost completely, and to provide a highly reliable positive displacement machine with extremely small vibration. It is to provide it, and to realize it at low cost.
[0005]
[Means for Solving the Problems]
To achieve the above object, the claims are independent claims. 1 The low-vibration positive displacement machine according to the invention is a structural part that should be stationary in each component. Material Have And two drive shafts that rotate in opposite directions and a mechanism that is driven by each of the drive shafts and consumes substantially the same amount of power, and the mechanism periodically changes the power consumption during steady operation. In a low-vibration positive displacement machine in which the structural members to be stationary are integrally fixed, the drive shafts are synchronized so that their phases are substantially equal. The mechanism that consumes power by being driven through the two drive shafts is a piston portion that is guided by other members to perform reciprocation and rotation around the axis in the reciprocation direction, and a direction perpendicular to the reciprocation direction. A reciprocating member composed of two arm portions projecting on opposite sides, a guide member which is another member for guiding the piston portion of the reciprocating member, and rotating in opposite directions around a coaxial rotation axis Times Two shaft members each supporting one of the arm portions of the reciprocating member at a position displaced in the radial direction from the shaft so as to be capable of relative rotation and change in the relative rotation axis direction; and the two shaft members A bearing member that supports the rotation of the two reciprocating members, forming a sealed space adjacent to the reciprocating member to form an operating space, and reciprocating the reciprocating member by rotating the two shaft members in opposite directions. It is a mechanism that moves and changes the volume of the working space to move and compress the working fluid. It is characterized by things.
[0006]
Similarly, claims 5 The low-vibration positive displacement machine according to the invention is a structural part that should be stationary in each component Material Have And two output shafts rotating in opposite directions to each other, and a mechanism for supplying substantially the same amount of power to the outside through the output shafts, and the mechanism periodically changes the output during steady operation. Having a synchronization mechanism that synchronizes the output shafts so that their phases are substantially equal, Structural members that should be stationary One It is characterized by being fixed to the body.
[0007]
[Action]
First, among several means for solving the above-described problems, two positive displacement machines or positive displacement engines whose consumption power or output changes approximately equally and periodically are respectively connected to the two shaft members. Let us consider a case where a positive displacement machine is configured by synchronizing the phases.
[0008]
In this case, an excitation torque that changes periodically is generated by the positive displacement machine or positive displacement engine connected to one shaft member, but at the same time, the positive displacement machine or positive displacement engine connected to the other shaft member. As a result, an exciting torque that changes in a cycle in a similar manner is generated. Moreover, since the two shaft members are always rotating in almost opposite directions in synchronism with each other, the above-described two excitation torques always change in opposite directions and in substantially the same size. Further, since the members to be stationary of the positive displacement machine or positive displacement engine are fixed to each other so as to be integrated, the above two excitation torques always cancel each other through the fixed portion, Excitation torque hardly acts on the externally mounted portion as the positive displacement machine, and the external vibration is eliminated. Therefore, it is not necessary to take measures against vibration isolation at the connecting portion with the outside. In addition, no matter how large the excitation torque generated by an individual positive displacement machine or positive displacement engine, it can be canceled out with approximately the same excitation torque, so the positive displacement machine or positive displacement engine used This structure does not require a large number of working chambers with different phases in order to reduce vibration, and can be a simple and inexpensive structure.
[0009]
Next, among several means for solving the above-described problems, a case where a positive displacement machine is configured by connecting two shaft members to a common positive displacement machine or positive displacement engine will be considered.
[0010]
Since this positive displacement machine has two similar drive shafts or output shafts rotating in opposite directions, the direction of the drive shaft or output shaft around the rotation axis is related to the operation of each component including its internal components. It can be made into a structure that does not have sex. That is, when viewed from the axial direction of the drive shaft or the output shaft, each component can be configured to perform a symmetric motion with respect to a certain axis. Therefore, if a mass having the same rotational inertia (moment of inertia) is attached to each of the two drive shafts or output shafts, and a similar drive source or load is connected, the signals are transmitted via the two drive shafts or output shafts. Driving torque or output torque can be made almost equal. At this time, this positive displacement machine is not only related to the operation of each part but also to the force acting on each part, it is always almost symmetric when viewed from the axial direction of the drive shaft or output shaft, and is generated as a result of the action of those forces. The excitation torque to be applied should have no directivity around the rotation axis of the drive shaft or output shaft.
[0011]
On the other hand, the excitation torque generated by a general positive displacement machine is always caused by fluctuations in the drive torque or output torque transmitted via the drive shaft or output shaft of the positive displacement machine. It is generated as fluctuating torque that tries to rotate the opponent around the axis. Even if there are two similar drive shafts or output shafts rotating in opposite directions, these shafts are coaxial or parallel to each other and have the same axial direction. It should be generated as a fluctuating torque that tries to rotate the opponent.
[0012]
However, when the value of the excitation torque is other than zero, the other end is rotated in the direction around the drive shaft or the output shaft, and the direction is directed. This contradicts the above-described logic that the direction of the drive torque or the output shaft around the rotation axis disappears due to the symmetry of the motion of each component. Therefore, the value of the excitation torque must be zero, and if the members to be stationary of this positive displacement machine are fixed to each other so as to be united, the mounting portion to the outside of the entire positive displacement machine Excitation torque is no longer applied to, and no external vibration is applied. Therefore, it is not necessary to take measures against vibration isolation at the connecting portion with the outside.
[0013]
In addition, no matter how large the fluctuations in the power consumed or supplied by this positive displacement machine, the excitation torque becomes zero regardless of this, so the structure of this positive displacement machine is phased to reduce vibration. It is not necessary to have many different working chambers, and a simple and inexpensive structure is sufficient. In this means, the symmetry of the motion of each component when viewed from the axial direction of the drive shaft or output shaft, the identity of the rotational inertia (moment of inertia) attached to each of the two drive shafts or output shaft, Even if the identity of the drive source or load connected to each of the two drive shafts or output shafts is not perfect, the excitation torque can be reduced if the symmetry and identity errors are kept small. Occurrence can be reduced to such an extent that it does not substantially become a problem.
[0014]
【Example】
Embodiments of the present invention will be described below with reference to FIGS. 1 is a cross-sectional view of a gas compressor, which is a positive displacement machine according to a first embodiment of the present invention, as viewed from above, FIG. 2 is a cross-sectional view taken along line II in FIG. 1, and FIG. 3 is a second embodiment of the present invention. FIG. 4 is a cross-sectional view of an engine power generator as an example of a positive displacement machine from above, FIG. 4 is a cross-sectional view along II-II in FIG. 3, and FIG. 5 is an engine power generator as a positive displacement machine of a third embodiment of the present invention. FIG. 6 is a sectional view of a gas compressor, which is a positive displacement machine according to a fourth embodiment of the present invention, viewed from the side, and FIG. 7 is a sectional view of the fifth embodiment of the present invention. FIG. 8 is a sectional view of a hermetic compressor as a positive displacement machine viewed from the side, FIG. 8 is a diagram illustrating the operating principle of the mechanism in FIG. 7, and FIG. 9 is a positive displacement machine according to a sixth embodiment of the present invention. FIG. 10 is a cross-sectional view of an open type compressor as viewed from the side, and FIG. 10 is a cross-sectional view of the engine generator as a positive displacement machine according to the seventh embodiment of the present invention as viewed from the side. FIG. 11 is a sectional view of an open type compressor as a positive displacement machine according to an eighth embodiment of the present invention as viewed from the side, and FIG. 12 shows an internal combustion engine as a positive displacement machine according to the ninth embodiment of the present invention. FIG.
[0015]
1 and 2 show a gas compressor which is a positive displacement machine according to a first embodiment of the present invention. The entirety of the present embodiment is composed of two compressor units each including a compression mechanism portion including a main shaft 1, a cylinder 2, a frame 3, a side cover 4, a swinging piston 5, a shoe 6 and the like, and an electric motor 7 for driving the compression mechanism portion. It is configured in combination. In the compression mechanism portion, the roller portion 5a of the swing piston 5 is rotatably inserted into the eccentric portion 1a of the main shaft 1 that is rotatably supported by the frame 3 and the side cover 4, and the vane portion 5b of the swing piston 5 is the shoe 6 It is restrained by the cylinder 2 via. When the roller portion 5a of the oscillating piston 5 revolves with the rotation of the main shaft 1, the cylinder 2 and the frame 3 fixed to each other by the roller portion 5a, the vane portion 5b, the shoe 6 and a bolt (not shown). By utilizing the fact that the volume of the space surrounded by the side cover 4 changes, the gas is sucked from the suction port 2a of the cylinder 2 and compressed, and then is discharged via the discharge port 2b, the discharge valve 8, and the discharge valve retainer 9. Are discharged.
[0016]
The two compressor units of the present embodiment, in which a driving motor 7 having a stator 7a and a rotor 7b is added to this, are the same, and the main shafts 1 that are their driving shafts are parallel to each other but face in opposite directions. Similarly, the mounting feet 3a of the respective frames 3 are fixed to the common frame 10 with bolts. The stator portions 7a of the two electric motors 7 are fixed to the two frames 3, respectively. Since the main shafts 1 are arranged so as to face in opposite directions and are driven by the same electric motor 7, they rotate in opposite directions in the assembled state as a whole gas compressor, but are timing gears fixed to one end of each. When the 11 meshes with each other, the phases of the compression mechanism portions that are driven by each of them are reversed in synchronism so that they always coincide with each other.
[0017]
In addition, in this invention, well-known things, such as a positive displacement pump and a Stirling refrigerator, are implemented as a positive displacement machine besides the vane type compressor shown by the said Example.
[0018]
According to the first embodiment, as described in the section of “Operation”, the excitation torques generated by the two positive displacement compressor units are reversed and in phase with each other, There is an effect that it is possible to hardly transmit the excitation torque to the outside from the common frame 10 which is a mounting portion to the outside. Further, in the first embodiment, two same compressor units having a simple structure conventionally used as individual compressor units may be combined, and extremely complete vibration reduction is relatively inexpensive. There is an effect that can be achieved. In the first embodiment, since the main shafts of the two compressor units are arranged so as to be parallel to each other, it is possible to easily synchronize the reversing shafts by using gears or the like. is there. Furthermore, there is an effect that the overall axial length can be reduced.
[0019]
FIGS. 3 and 4 show an engine power generator as a positive displacement machine according to a second embodiment of the present invention. The entirety of the present embodiment includes a crankshaft 12, a cylinder block 13, a cylinder head 14, a bearing frame 15, a side cover 16, a connecting rod 17, a piston 18, a piston pin 19, a spark plug 20, a suction valve 21, a discharge valve 22, and a motion. It is configured by combining two engine generator units composed of a four-cycle one-cylinder internal combustion engine section configured by a valve mechanism (not shown) and the like and a generator 23 or 24 driven thereby. Since a four-cycle internal combustion engine is generally well known, the description of its operating principle is omitted. However, the two internal combustion engines used in the second embodiment use common parts, but the cylinder head 14, the intake valve 21, the discharge valve 22, and the motor are used during assembly. By changing the fixing direction of a valve mechanism (not shown) or the like, the structure reverses to each other.
[0020]
Further, the generator 23 and the generator 24 are used in such a manner that the rotation direction when generating power is opposite to the rotation direction of the internal combustion engine. The two engine generator units are reverse to each other, and the mounting feet 15a of the respective bearing frames 15 are connected to the common frame by bolts so that the crankshafts 12 as drive shafts thereof are parallel to each other and face the same direction. 25 is fixed. The stator portions 23a and 24a of the two generators 23 and 24 are fixed to the two bearing frames 15, respectively, and the rotor portions 23b and 24b are fixed to the two crankshafts 12, respectively. Two cylinder blocks 13 are fixed to the two bearing frames 15 respectively. The crankshafts 12 are arranged so that the crankpin portions 12a are located in the same direction end portions and face the same direction and are driven in the opposite directions by the respective internal combustion engines. Although they rotate in opposite directions, when the timing gears 26 fixed to the respective ends mesh with each other, they rotate in synchronism so that the phases of the internal combustion engine parts that drive them always coincide with each other.
[0021]
In the present invention, as a positive displacement engine, in addition to the four-stroke engine in the one-side working chamber of the above embodiment, the one in the upper and lower working chambers, the two-stroke internal combustion engine, the external combustion engine, The engine can be implemented by connecting various known generators and turbo compressors.
[0022]
Also in the second embodiment, as described in the section of “Operation”, the excitation torques generated by the two engine generator units are opposite to each other so as to cancel out each other, and to the outside. There is an effect that the excitation torque can be hardly transmitted from the common frame 25 which is the mounting portion. In the second embodiment, an internal combustion engine having a simple structure that has been conventionally used may be used as each internal combustion engine, and an extremely complete low vibration can be achieved at a relatively low cost. . Further, in the second embodiment, since the main shafts of the two generator units are arranged so as to be parallel to each other, it is possible to easily synchronize the reversing ones by using gears or the like. is there. Furthermore, there is an effect that the overall axial length can be reduced.
[0023]
FIG. 5 shows a power generator as a positive displacement machine according to a third embodiment of the present invention. The entirety of the present embodiment includes a crankshaft 12, a cylinder block 13, a cylinder head 14, a bearing frame 15, a side cover 16, a connecting rod 17, a piston 18, a piston pin 19, a spark plug 20, a suction valve 21, a discharge valve 22, and a motion. Two generator units each including a four-cycle one-cylinder internal combustion engine section configured by a valve mechanism (not shown) and the like and a generator 23 driven thereby are combined. The two internal combustion engines used in the third embodiment use common parts, and unlike the case of the second embodiment, the assembly is performed in exactly the same manner. The rotation direction of the crankshaft 12, which is the output shaft, is also the same. That is, they are exactly the same thing. Therefore, the generator 23 driven thereby uses two identical objects. The mounting legs 15a of the two bearing frames 15 are fixed to the common frame 27 with bolts so that the crankshafts 12 of the two generator units are coaxially arranged in opposite directions. The crankshafts 12 are driven in the same direction by the respective internal combustion engines, but are arranged so as to face in opposite directions to each other, and thus rotate in the opposite directions in the assembled state as the entire power generation device. Further, the timing gears 28 of the bevel gears fixed to the respective ends mesh with each other via the intermediate gear 29 of the bevel gears, so that the phases of the internal combustion engine parts that drive the gears are synchronized with each other so that the phases of the internal combustion engine parts always coincide with each other. Rotate in the opposite direction. The intermediate gear 29 is rotatably supported by a support shaft 30 fixed to the common frame.
[0024]
Also according to the third embodiment, as described in the section of “Action”, the excitation torque generated by the two generator units is reversed and in phase with each other so that they can be canceled out and attached to the outside. There is an effect that it is possible to hardly transmit the excitation torque from the common frame 27 as a part. In the third embodiment, two identical internal combustion engines that have been conventionally used as individual internal combustion engines may be used, and a very complete low vibration can be achieved at a relatively low cost. There is an effect that can be achieved. Further, in the third embodiment, since the main shafts of the two generator units are arranged coaxially, there is an effect that the width in the direction perpendicular to the axis as the entire power generator can be reduced.
[0025]
FIG. 6 shows a gas compressor which is a positive displacement machine according to a fourth embodiment of the present invention. The entirety of the present embodiment is composed of a compression mechanism portion of the same type as that of the first embodiment, which includes a main shaft 31, a cylinder 32, a frame 33, a side cover 34, a swinging piston 35, a shoe (not shown), and the like. Shaft 36, cylinder block 13, cylinder head 14, bearing frame 37, side cover 38, connecting rod 17, piston 18, piston pin 19, spark plug 20, intake valve 21, discharge valve 22, valve operating mechanism (not shown), etc. The four-cycle one-cylinder internal combustion engine section of the same type as in the second and third embodiments is configured by combining two compressor units that are driven via an Oldham joint 39.
[0026]
However, the two compression mechanism parts used in the fourth embodiment use the same individual parts, but by changing the fixing direction of the parts such as the cylinder 32 during assembly. The two internal combustion engine parts are also used in the same direction as in the second embodiment, but the parts are the same as in the case of the second embodiment. It has a structure. That is, the two compressor units have a structure in which their rotating shafts rotate in opposite directions. At that time, the compression mechanism portion and the internal combustion engine portion are connected by the Oldham coupling 39 so that the relationship between the phase of the compression mechanism portion and the phase of the internal combustion engine portion is substantially equal between the two compressor units. ing.
[0027]
In this embodiment, the two compressor units are fixed to the common frame 40 so that their rotation axes are coaxial and face the same direction. As a result, the rotating shafts rotate in opposite directions even when assembled as a whole compressor. Furthermore, the main shaft 31 of one compressor unit and the crankshaft 36 of the other compressor unit are connected by a reverse coupling 41, and the compression mechanism portions and the internal combustion engine portions of the two compressor units are in phase with each other. Are rotated in the opposite direction to each other at almost the same time. The reversing joint 41 is composed of a reciprocating member 42, a guide member 43, a disk member 44, and a spherical bush 45. The reciprocating member 42 is guided by the guide member 43 through its piston portion 42a to reciprocate and reciprocate. When the two spherical bushes 45 into which the two arm portions 42b of the reciprocating member 42 are inserted revolve in opposite directions, the spherical bush 45 can be oscillated. The two disk members 44 to be supported and the shaft members to which they are fixed are connected so as to rotate in the opposite directions at the same speed. This mechanism is used as a mechanism of a positive displacement compressor body in the fifth embodiment of the present invention to be described later, and its principle is illustrated in FIG.
[0028]
Also according to the fourth embodiment, as described in the section of “Operation”, the excitation torque generated by the two compressor units is reversed to be in phase with each other, thereby canceling each other out. There is an effect that it is possible to hardly transmit the excitation torque from the common frame 40 which is a mounting portion to the outside of the frame. In addition, this cancels out each other by making both the excitation torques generated by the compression mechanism units of the two compressor units and the excitation torques generated by the internal combustion engine parts in opposite directions and in the same phase, In other words, it can be paraphrased that almost no excitation torque can be transmitted from the common frame 40 which is a mounting portion to the outside of the entire embodiment. In the fourth embodiment, a simple structure conventionally used as an individual compression mechanism or an internal combustion engine may be used, and extremely low vibration can be achieved at a relatively low cost. There is an effect. In the fourth embodiment, since the main shafts of two compressor units are coaxially arranged, there is an effect that the width of the whole compressor in the direction perpendicular to the axis can be reduced.
[0029]
In the positive displacement machines of the first to fourth embodiments so far, each of the two combinations of the machine and the engine that drives the same is prepared to constitute a low vibration positive displacement machine as a whole. However, as long as at least one of the machine and the engine / structure of the machine and engine is satisfied, it can be replaced with any other machine / engine of the other system / structure. Machine vibration can be reduced. In addition, the machine and the engine, which are those components, were integrated by being fixed to a common frame, but even if these components are directly fixed and integrated, they are similarly low vibration. The positive displacement machine is obtained.
[0030]
7 and 8 show a hermetic compressor as a positive displacement machine according to a fifth embodiment of the present invention. The reciprocating member 46 is supported so that the two piston portions 46a are guided by the inner peripheral cylindrical surface 47a of the cylinder block 47 so as to perform reciprocating motion and rotation around the axis in the reciprocating direction. Two columnar arm portions 46b projecting in opposite directions perpendicular to the reciprocating direction are fixed to the piston portion 46a of the reciprocating member 46 by press fitting and nuts 46c. The spherical bush 48 is rotatably inserted into the inner peripheral cylindrical surface portion. The outer peripheral spherical surface portions of the two spherical bushes 48 are supported by spherical pairs at positions displaced from the rotation shaft of the drive shaft 49 by the drive arm portions 49a of the drive shaft 49, respectively.
[0031]
As a result, the two arm portions 46b of the reciprocating member and the two drive shafts 49 are coupled at a position displaced from the rotation shaft of the drive shaft 49 so that the relative rotation and the relative tilt direction change are possible. ing. On the opposite side of the drive arm 49a in the radial direction of the drive shaft 49, a balance mass 49b is formed. The two drive shafts 49 are rotatably supported by bearing portions 50a of the bearing frame 50, respectively. The two bearing frames 50 are fixed to the cylinder block 47 by bolts (not shown) so that the central axes of the bearing portions 50a are coaxially arranged. The central axes of the two inner peripheral cylindrical surfaces 47a formed in the cylinder block 47 are also coaxial with each other, and further, are perpendicular to the central axis of the bearing portion of the bearing frame 50 fixed to the cylinder block 47. ing.
[0032]
The opening end of the inner peripheral cylindrical surface 47 a of the cylinder block 47 is closed by the cylinder head 51, and the working chamber 52 surrounded by the piston portion 46 a of the reciprocating member, the inner peripheral cylindrical surface 47 a of the cylinder block, and the cylinder head 51. Two are formed. A suction passage 46d to the working chamber 52 is formed in the piston portion 46a of the reciprocating member, and a suction valve 53 for opening and closing the suction passage 53 is mounted. A discharge port 51a is formed in the cylinder head 51, and a discharge valve 54 for opening and closing the port is mounted. A high pressure chamber cover 55 is fixed outside the cylinder head 51, and a high pressure space 56 is formed between them.
[0033]
A stator portion 57a of a drive motor 57 is fixed to each of the two bearing frames by bolts, and a rotor of the drive motor 57 is opposite to the drive arm portion 49a with the two drive shafts 49 sandwiching the bearing portion 50a. The part 57b is fixed. A balance mass 58 that generates a smaller centrifugal force in the opposite direction to the balance mass 49b is attached to the rotor portion 57b. The two drive motors 57 constituted by the stator portion 57a and the rotor portion 57b are the same, but are incorporated in the overall configuration of the above-described compressor so as to face each other. Are rotated in opposite directions. These components are fixed to the inner periphery of the central chamber 59 by shrink fitting or the like, and are further housed in a sealed container including the central chamber 59 and two end chambers 60 on both sides thereof.
[0034]
FIG. 8 shows the movement of each movable part when the two drive shafts 49 are driven in reverse to each other. (A) to (e) in FIG. 8 are movements of the movable parts as viewed from the right direction in FIG. 7, and (a ′) to (e ′) are as viewed from above (a) to (e), respectively. FIG. The two spherical bushings 48 are supported by spherical pairs at positions displaced in the radial direction from the rotation axis (point A) of the drive shaft 49, so that when the two drive shafts 49 rotate in opposite directions, their centers ( As shown in FIGS. 8A to 8E, the points B and C) revolve around the rotation axis (point A) at the same revolution radius and in the opposite direction.
[0035]
Since the reciprocating member 46 cannot be tilted from the vertical reciprocating direction axis in FIGS. 8A to 8E, the two columnar arm portions 46b are always perpendicular to the reciprocating direction axis, ie, FIG. In, it must face the horizontal direction. Accordingly, the vertical coordinates in FIGS. 8A to 8E of the two centers (point B and point C) of the spherical bush 48 into which the cylindrical arm portion 46b is inserted are always equal.
[0036]
On the other hand, since the reciprocating member 46 can rotate around the reciprocating direction axis, the columnar arm portion 46b is centered on the reciprocating direction axis (point D) shown in FIGS. 8 (a ') to (e'). The swing motion is performed. Therefore, the left and right direction coordinates in FIGS. 8A to 8E of the two centers (point B and point C) of the spherical bush 48 into which the arm portion 46b is inserted are opposite in sign.
[0037]
In this embodiment, the above relationship is always forced to the two-dimensional coordinates in FIGS. 8A to 8E at the centers (points B and C) of the two spherical bushes 48. The two built-in drive shafts 49 are not only driven in opposite directions by the respective drive motors 57 but also rotate in complete synchronization with each other. At that time, the reciprocating member 46 also has a periodic reciprocating motion in the vertical direction as the two spherical bushes 48 supporting the reciprocating member 46 change the same period with respect to the vertical coordinate in FIGS. 8 (a) to 8 (e). The volume of the two working chambers 52 formed above and below is periodically changed.
[0038]
The working gas flows into the low pressure space 62 inside the sealed container from the low pressure pipe 61 attached to the central chamber 59 and is sucked into the working space 52 via the suction passage 46d of the piston portion 46a of the reciprocating member and the suction valve 53. And is discharged to the high pressure space 56 through the discharge port 51a of the cylinder head and the discharge valve 54, and flows out from the high pressure space 56 through the central chamber 59 to the outside through the high pressure pipe 63. .
[0039]
In this embodiment, the two drive shafts 49 and the rotor portion 57b of the drive motor are reversed, and the other movable parts also move as shown in FIGS. 8A to 8E. When viewed, the two-dimensional motion of each part of the compressor can be made to be completely symmetric motion with the vertical central axis in each of FIGS. 8A to 8E as the symmetry axis. Further, since the mass having the same rotational inertia (moment of inertia) is attached to each of the two drive shafts 49 and they are driven by the motor having the same power, the compressor according to the present embodiment operates each component. As for the force acting on each part as well as with respect to the direction of the drive shaft, it is always symmetrical with respect to the symmetry axis as viewed from the direction of the drive shaft, and the excitation torque generated as a result of the action of these forces is the direction around the rotation axis of the drive shaft. The excitation torque should not be generated. That is, according to the present embodiment, there is an effect that no excitation torque is generated due to periodic fluctuations in the power for driving the positive displacement compressor although it is a positive displacement compressor.
[0040]
Next, in this embodiment, the inertia force (the vertical direction in FIG. 7) of the reciprocating motion of the reciprocating member 46 is the sum of the reciprocating motion direction components of the centrifugal force of the balance masses 49b and 59 attached to the two drive shafts 49. Simultaneously with the cancellation, the component perpendicular to the reciprocating direction of the centrifugal force (the vertical direction in FIG. 7) can be canceled out by utilizing the fact that the two drive shafts 49 are reversed. Further, as shown in FIGS. 8 (a ') to (e'), the inertial couple generated by the reciprocating member 46 swinging around the reciprocating direction axis (point D) is also driven by each. By shifting the resultant action point of the centrifugal force of the balance mass 49b fixed to the shaft 49 and the centrifugal force of the mass 58 in the axial direction (left-right direction in FIG. 7), a component perpendicular to the reciprocating direction of the centrifugal force (see FIG. It can be almost canceled by a couple of forces in the direction perpendicular to the 7th page. That is, according to the present embodiment, there is an effect that generation of unbalanced inertia force can be prevented almost completely despite the reciprocating mechanism. In order to cancel both of the inertia force of the reciprocating motion and the inertia couple of the swing motion of the reciprocating member 46 at the same time, it is necessary to attach the two balancing masses 49b and 58 to the respective drive shafts 49.
[0041]
Next, in this embodiment, the reciprocating member 46 is driven by two drive motors 57 that generate substantially the same driving torque, and therefore acts on the inertia force of the reciprocating motion of the reciprocating member 46 and its piston portion 46a. The compressive load due to the pressure of the working gas is applied with almost equal force through the two spherical bushes 48 in which the two arm portions 46b are separated from the center of action of the inertia force and the compressive load (point D in FIG. 8) by approximately equal distance. It is supported. In other words, even if no supporting force is applied from other members, it is possible to balance them only with those forces. Therefore, there is no load between the piston portion 46a of the reciprocating member and the inner peripheral cylindrical surface 47a of the cylinder block 47. Does not work. That is, since the piston side force, which is one of the causes of mechanical friction loss in the conventional reciprocating mechanism, does not occur, the mechanical friction loss is reduced and the efficiency is improved.
[0042]
Next, this embodiment differs from the previous first to fourth embodiments in that each of the two machines and the engine for driving the machine is required. Since it is configured by a machine and also serves as a reverse synchronization mechanism, the number of components as a whole compressor can be reduced. That is, there is an effect that it can be produced at low cost.
[0043]
Furthermore, in this embodiment, there is an effect that the width and diameter in the direction perpendicular to the axis of the compressor can be reduced.
[0044]
FIG. 9 shows an open type compressor which is a positive displacement machine according to a sixth embodiment of the present invention. The central compressor section includes a reciprocating member 46, a cylinder block 64, a spherical bush 48, a drive shaft 65, a bearing frame 66, a cylinder head 51, a suction valve 53, a discharge valve 54, and the like in the fifth embodiment of FIG. A similar mechanism is used to compress the working gas by changing the volume of the working chamber 67. The drive source includes a crankshaft 36, a cylinder block 13, a cylinder head 14, a bearing frame 37, a side cover 38, a connecting rod 17, a piston 18, a piston pin 19, a spark plug 20, a suction valve 21, a discharge valve 22, and a valve. Two four-cycle one-cylinder internal combustion engine sections composed of a mechanism (not shown) and the like are prepared, and a crankshaft 36 as an output shaft thereof is connected to a drive shaft 65 from both sides via an Oldham joint 39. Yes. At that time, the two internal combustion engine parts are connected so as to have the same phase. The two internal combustion engine portions are the same, but are incorporated in the entire open type compressor so as to face each other, so that the output shafts are reverse to each other. Further, the stationary members in the above-described components are fixed integrally with each other by fixing the bearing frames 66 and 37 to the common frame 68. In the present embodiment, both the compressor section that consumes power and the internal combustion engine section that drives it are of the positive displacement type, but the compressor section does not generate an excitation torque with the same logic as in the fifth embodiment. Since the excitation torques of the two internal combustion engine portions are opposite in direction and synchronized in phase, they cancel each other out, and there is an effect that no excitation torque is generated as a whole.
[0045]
In addition, in this embodiment, no electric machine is used in the part that consumes power or the part that supplies the power, and no equipment such as power supply or power transmission is required, and it contributes to power peak cut by not consuming electric power. There is an effect that can be done.
[0046]
In addition, if the compressor unit is used as a refrigerator for the refrigeration cycle in this embodiment, the waste heat of the internal combustion engine unit can be directly assembled in the form of heat with a heat pump and used during heating operation, and the power source is also There is an effect that the overall energy efficiency including the energy can be improved.
[0047]
Furthermore, according to the present embodiment, the piston side force is not generated in the compressor section, the mechanical friction loss is reduced and the efficiency is improved, the effect that the number of components can be reduced, and the compressor shaft can be produced at a low cost. The effect that the width and diameter in the perpendicular direction can be reduced can be obtained as in the fifth embodiment.
[0048]
FIG. 10 shows a power generator as a positive displacement machine according to a seventh embodiment of the present invention. In the central internal combustion engine section, the reciprocating member 69 has its main piston portion 69a and sub-piston portion 69b guided by the inner peripheral cylindrical surfaces 70a and 70b of the cylinder block 70, respectively, so that the reciprocating motion and the reciprocating motion around the axis in the reciprocating direction are performed. It is supported so that it can rotate. The members forming the main piston portion 69a and the sub-piston portion 69b of the reciprocating member 69 have two columnar arm portions 69c projecting in opposite directions in the direction perpendicular to the reciprocating motion direction. The arm portions 69c are rotatably inserted into the inner peripheral cylindrical surface portion of the spherical bush 71, respectively.
[0049]
The outer peripheral spherical surface portions of the two spherical bushes 71 are supported by spherical pairs at positions displaced in the radial direction from the rotation axis of the main shaft 72 by output arm portions 72a of the main shaft 72, respectively. As a result, the two arm portions 69c of the reciprocating member and the two main shafts 72 are coupled at a position deviated from the rotation shaft of the main shaft 72 so that the relative rotation and the relative inclination direction can be changed. Yes.
[0050]
A counterweight 72b is attached to the opposite side of the main arm 72 in the radial direction of the output arm portion 72a. The two main shafts 72 are rotatably supported by bearing portions 73a of the bearing frame 73, respectively. The two bearing frames 73 are respectively fixed to the cylinder block 70 with bolts (not shown) so that the central axes of the bearing portions 73a are coaxially arranged, and two cylinder blocks 70 are coaxial with each other. The inner circumferential surfaces 70a and 70b are orthogonal to the central axis.
[0051]
The opening end of the inner peripheral cylindrical surface 70a of the cylinder block 70 is closed by a cylinder head 74, and a working chamber 75 surrounded by the main piston portion 69a of the reciprocating member, the inner peripheral cylindrical surface 70a and the cylinder head 74 is one. One is formed. The cylinder head 74 is formed with two suction ports and two discharge ports, and a suction valve 76, a discharge valve 77, a spark plug 78, a valve operating mechanism (not shown) and the like are mounted for opening and closing the port.
[0052]
FIG. 10 shows one intake valve 76 and one discharge valve 77 far from the cross section, but another discharge valve is on the near side of the cross section of the suction valve 76 and is on the near side of the cross section of the discharge valve 77. Another intake valve is mounted on each side. That is, two suction ports 76 and two suction valves 76 that open and close the discharge port around the spark plug 78 and the discharge valves 77 are arranged at point-symmetric positions. The inner peripheral cylindrical surface 70b of the cylinder block 70 fulfills only the function of guiding the reciprocating motion of the sub-piston portion 69b. One end of the cylinder block 70 is left open and no working chamber is formed. Cycle 1 cylinder.
[0053]
The mechanism is the same as that of the central compressor portion of the fifth embodiment shown in FIG. 7, and the two main shafts 72 are reversed in synchronization with each other for the same reason as described in the fifth embodiment. It is possible to eliminate the generation of excitation torque from the engine unit. A rotor portion 79 a of a generator 79 is fixed to one end of each of the two main shafts 72 that are reversed in synchronization with each other, and a stator portion 79 b is fixed to the bearing frame 73. Although a known DC type or AC type generator is implemented, detailed components such as wiring and brushes are not shown. In the case of an AC generator, the positions of the rotor portion 79a and the stator portion 79b around the main shaft 72 are fixed so that the phases of the AC outputs of the two generators 79 are substantially equal. Note that a balance mass 80 that generates a smaller centrifugal force in the opposite direction to the balance mass 72b is attached to the rotor portion 79a. The two AC generators 79 have exactly the same specifications, but are installed facing each other, so that they can be driven in the same manner by the two main shafts 72 that are reversed, and each is generated due to equal phases. Excitation torque can cancel each other. According to the present embodiment, an effect that no excitation torque is generated despite being a positive displacement machine, an effect that generation of an unbalanced inertia force can be prevented almost completely despite a reciprocating mechanism, and a piston side The effect of reducing the mechanical friction loss and improving the efficiency without generating force, the effect of being able to produce at low cost with few components, and the effect of being able to keep the width and diameter of the generator perpendicular to the axis small. This is obtained for the same reason as described in the fifth embodiment.
[0054]
FIG. 11 shows an open type compressor which is a positive displacement machine according to an eighth embodiment of the present invention. The central internal combustion engine section is a four-cycle one-cylinder positive displacement internal combustion engine that is substantially equal to the seventh embodiment of FIG. 10, but the two output shafts 81 are different in volume from the AC generator of the seventh embodiment. Each type of compressor section is connected via an Oldham coupling 39. The two compressor sections are positive displacement compressors substantially the same as those of the first embodiment of the present invention shown in FIG. 1, but when the drive shaft 82 is connected to the output shaft 81 of the internal combustion engine via the Oldham coupling 39. The rotational phase of the two compressor sections is approximately equal to each other and connected to the output shaft 81.
[0055]
In the present embodiment, first, both the compressor section that consumes power and the internal combustion engine section that drives the compressor section are of the positive displacement type, but the internal combustion engine section does not generate an excitation torque for the same reason as in the fifth embodiment. In addition, since the excitation torques of the two compressor sections are opposite in direction and synchronized in phase, they cancel each other, and there is an effect that no excitation torque is generated as a whole.
[0056]
Further, according to the present embodiment, the piston side force of the internal combustion engine part is not generated, the mechanical friction loss is reduced and the efficiency is improved, the effect that the number of components can be reduced and the production can be performed at a low cost, the shaft of the power generator The effect that the width and diameter in the perpendicular direction can be reduced can be obtained for the same reason as described in the fifth embodiment.
[0057]
Further, in this embodiment, as in the sixth embodiment, there is no need for equipment such as a power source and power transmission, and the effect that it can contribute to the peak power cut and the waste heat of the internal combustion engine section are utilized for the heating operation. There is an effect that the energy efficiency of can be improved.
[0058]
FIG. 12 shows an internal combustion engine as a ninth embodiment of the present invention. This embodiment has the same mechanism as that of the internal combustion engine portion which is a drive source in the power generation apparatus of the seventh embodiment and the compressor of the eighth embodiment, but two intermediate output shafts that are reverse to each other. 83 is finally connected to one final output shaft 84, and has a versatility as a structure for driving various machines with one output shaft rotating in one direction as in a conventional ordinary internal combustion engine. is there. A rotary inertia mass 85 is fixed to each of the two intermediate output shafts 83, and a bevel gear gear 87 is coaxially mounted via a flexible member 86 such as rubber or a spring that enables relative twisting. ing. The two bevel gears 87 jointly rotate in reverse with each other and rotate the bevel gear 88 fixed to the final output shaft 84. The final bearing frame 89 that rotatably supports the final output shaft 84 has a structure that can rotate around the rotation shaft of the intermediate output shaft 83, that is, the rotation shaft of the bevel gear 87, and is rotated by a stationary frame (not shown). It is supported freely and the same power is always transmitted from the two bevel gears 87 to the final output shaft 84.
[0059]
The power generated by the positive displacement engine fluctuates periodically. However, in the seventh and eighth embodiments, the power around the output shaft can be obtained by taking out the power with the two output shafts that are reverse to each other. It did not have directionality and prevented the generation of excitation torque. In this embodiment, the intermediate output shaft 83, which is two output shafts that are reversed in the middle, does not have directionality, but at the stage of the final output shaft 84, one shaft rotates in one direction and the directionality is reduced. Therefore, an excitation torque is generated due to the periodic fluctuation of the generated power. The excitation torque is reduced for the following reason.
[0060]
First, in this embodiment, a flexible member 86 is incorporated between the intermediate output shaft 83 and the final output shaft 84, and the intermediate output shaft 83 to which the large rotary inertia mass 85 is fixed is relative to the final output shaft 84. Therefore, the output torque fluctuation caused by the power fluctuation generated by the internal combustion engine is considerably mitigated by the inertia torque generated by the rotation fluctuation of the rotary inertia mass and transmitted to the final output shaft 84. Is done. In the internal combustion engine of this structure, the excitation torque is not generated at the stage where the output is transmitted to the intermediate output shaft 83 due to the symmetry of the structure, and the reaction of the torque that tries to drive the final output shaft 84 in a certain direction thereafter. However, since the fluctuation of the output torque transmitted to the final output shaft 84 is considerably reduced as described above, the vibration torque is also reduced.
[0061]
In order to reduce vibration in a conventional positive displacement engine, an increase in cost due to the increase in the number of cylinders is unavoidable. However, according to the present embodiment, the vibration is increased without an increase in the cost due to the increase in the number of cylinders. It is possible to provide a small displacement type engine.
[0062]
【The invention's effect】
ADVANTAGE OF THE INVENTION According to this invention, the excitation force resulting from the torque fluctuation in a positive displacement machine can be eliminated almost completely, and there exists an effect that a positive displacement machine with an extremely low vibration can be provided.
[0063]
That is, the two excitation torques always cancel each other out via the fixed portion, and the excitation torque hardly acts on the externally mounted portion as the whole positive displacement machine, and the outside can be vibrated. Disappear. Therefore, it is not necessary to take measures against vibration isolation at the connecting portion with the outside. In addition, no matter how large the excitation torque generated by an individual positive displacement machine or positive displacement engine, it can be canceled out with approximately the same excitation torque, so the positive displacement machine or positive displacement engine used This structure does not require a large number of working chambers with different phases in order to reduce vibration, and can be a simple and inexpensive structure.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a gas compressor as a positive displacement machine according to a first embodiment of the present invention as viewed from above.
FIG. 2 is a cross-sectional view taken along the line II in FIG.
FIG. 3 is a sectional view of an engine power generator as a positive displacement machine according to a second embodiment of the present invention as viewed from above.
4 is a sectional view taken along line II-II in FIG.
FIG. 5 is a cross-sectional view of an engine power generator as a positive displacement machine according to a third embodiment of the present invention as viewed from the side.
FIG. 6 is a sectional view of a gas compressor, which is a positive displacement machine according to a fourth embodiment of the present invention, as viewed from the side.
FIG. 7 is a cross-sectional view of a hermetic compressor as a positive displacement machine according to a fifth embodiment of the present invention when viewed from the side.
8 is a diagram illustrating the operating principle of the mechanism in FIG.
FIG. 9 is a cross-sectional view of an open type compressor that is a positive displacement machine according to a sixth embodiment of the present invention when viewed from the side.
FIG. 10 is a sectional view of an engine power generator as a positive displacement machine according to a seventh embodiment of the present invention as viewed from the side.
FIG. 11 is a cross-sectional view of an open type compressor that is a positive displacement machine according to an eighth embodiment of the present invention when viewed from the side.
FIG. 12 is a sectional view showing an internal combustion engine which is a positive displacement machine according to a ninth embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Main shaft, 1a ... Eccentric part, 2 ... Cylinder, 2a ... Intake port, 2 ... Discharge port b, 3 ... Frame, 3a ... Mounting foot part, 4 ... Side cover, 5 ... Swing piston, 5a ... Roller part, 5b ... vane part, 6 ... shoe, 7 ... electric motor, 7a ... stator part, 8 ... discharge valve, 9 ... discharge valve holder, 10 ... common frame, 11 ... timing gear, 12 ... crankshaft, 12a ... crankpin part, DESCRIPTION OF SYMBOLS 13 ... Cylinder block, 14 ... Cylinder head, 15 ... Bearing frame, 16 ... Side cover, 17 ... Connecting rod, 18 ... Piston, 19 ... Piston pin, 20 ... Spark plug, 21 ... Suction valve, 22 ... Discharge valve, 23 ... Generator, 23a ... Stator part, 23b ... Rotor part, 24 ... Generator, 24a ... Stator part, 24b ... Rotor part, 25 ... Common frame, 26 ... Timing gear, 27 Common frame 28 ... Timing gear 29 ... Intermediate gear 30 ... Support shaft 31 ... Main shaft 31a ... Eccentric part 32 ... Cylinder 33 ... Frame 34 ... Side cover 35 ... Swing piston 36 ... Crankshaft 36a ... Crank pin part, 37 ... Bearing frame, 38 ... Side cover, 39 ... Oldham joint, 40 ... Common frame, 41 ... Reverse joint, 42 ... Reciprocating member, 42a ... Piston part, 42b ... Arm part, 43 ... Guide member, 44 ... disk member, 45 ... spherical bush, 46 ... reciprocating member, 46a ... piston part, 46b ... arm part, 46c ... nut, 46d ... suction passage, 47 ... cylinder block, 47a ... inner peripheral cylindrical surface, 48 ... spherical bush, 49 ... drive shaft, 49a ... drive arm part, 49b ... balance mass, 50 ... bearing frame, 50a ... bearing part, 5 ... Cylinder head, 52 ... Working chamber, 53 ... Suction valve, 54 ... Discharge valve, 55 ... High pressure chamber cover, 56 ... High pressure space, 57 ... Driving motor 57, 57a ... Stator part, 57b ... Rotor part, 58 ... Balance Mass, 59 ... central chamber, 60 ... end chamber, 61 ... low pressure piping, 62 ... low pressure space, 63 ... high pressure piping, 64 ... cylinder block, 65 ... drive shaft, 66 ... bearing frame, 67 ... working chamber, 68 ... Common frame 69 ... reciprocating member 69a ... main piston part 69b ... sub piston part 69c ... arm part 69d ... nut 70 ... cylinder block 70a ... inner peripheral cylindrical surface 70b ... inner peripheral cylindrical surface 71 ... spherical bush, 72 ... main shaft, 72a ... output arm part, 72b ... balance mass, 73 ... bearing frame, 73a ... bearing part, 74 ... cylinder head, 75 ... working chamber, 76 DESCRIPTION OF SYMBOLS ... Suction valve, 77 ... Discharge valve, 78 ... Spark plug, 79 ... Alternator, 79a ... Rotor part, 79b stator part, 80 ... Balance mass, 81 ... Output shaft, 82 ... Drive shaft, 83 ... Intermediate output shaft, 84 ... Final output shaft, 85 ... Rotational inertia mass, 86 ... Flexible member, 87 Bevel gear, 88 ... Bevel gear, 89 ... Final bearing frame
A: Rotation axis of drive shaft 49, B: Center of spherical bush 48, C: Center of spherical bush 48, D: Reciprocating direction axis of reciprocating member 46

Claims (10)

Each having a structural member to be stationary for in the components and having a mechanism for consumption and two drive shafts rotating in opposite directions, about the same amount of power is driven by the respective drive shaft In addition, the mechanism includes a synchronization mechanism that synchronizes the drive shafts so that the phase of the periodic change in power consumption during steady operation is substantially equal, and the structural members to be stationary are integrated. In a low vibration positive displacement machine fixed to
A mechanism that consumes power by being driven through two drive shafts that rotate in opposite directions is a piston portion that is guided by another member to perform reciprocating motion and rotation about an axis in the reciprocating motion direction, and the reciprocating motion. A reciprocating member composed of two arm portions projecting in opposite directions at right angles to the direction, a guide member which is another member for guiding the piston portion of the reciprocating member, and directions opposite to each other around a coaxial rotation axis Two shaft members which support one of the arm portions of the reciprocating member at a position deviated from the rotation axis in a radial direction while rotating in a rotational direction and a change in the relative rotation axis direction. A bearing member for supporting the rotation of the two shaft members as a component, forming a sealed space adjacent to the reciprocating member as an operating space, and by rotating the two shaft members in opposite directions. The reciprocating member Back and forth motion to change the volume of the working space, low vibration displacement machine, characterized in that a mechanism for the transfer and compression of the working fluid. According to claim 1, low vibration displacement machine, characterized in that a structure driven by a non-displacement type engine unit such two shaft members, respectively It electric motor and the turbine rotating in opposite directions. 2. The low-vibration positive displacement machine according to claim 1, wherein the two shaft members rotating in opposite directions are driven by positive displacement engine units such as an internal combustion engine, an external combustion engine, and a hydraulic motor . 4. The two positive displacement engine units that drive shaft members rotating in opposite directions to each other are connected to the shaft member in a state in which the phases of periodic changes in output are substantially equal to each other. Low vibration positive displacement machine. Each of the components has a structural member to be stationary, has two output shafts that rotate in opposite directions, and a mechanism that supplies substantially the same amount of power to the outside via the output shafts. In addition, the mechanism includes a synchronization mechanism that synchronizes the output shafts so that the phase of the periodic change of the output during steady operation is substantially equal, and the structural members to be stationary are integrated with each other. Low vibration positive displacement machine characterized by being fixed . 6. The mechanism according to claim 5, wherein the mechanism for supplying power to the outside through two output shafts rotating in opposite directions is guided by another member to perform reciprocating motion and rotation about an axis in the reciprocating direction. A reciprocating member composed of two arms projecting in opposite directions perpendicular to the reciprocating direction, a guide member as another member for guiding the piston portion of the reciprocating member, and a coaxial rotation axis Two reciprocating members that support relative rotation and change in the direction of the relative rotational axis at positions displaced in the radial direction from the rotational axis while rotating in opposite directions are supported. A shaft member and a bearing member that supports the rotation of the two shaft members are included as components, and a sealed space is formed adjacent to the reciprocating member to form a working space. Change volume and before Low vibration displacement machine, characterized in that the reciprocating member is reciprocated a mechanism for rotating the two shaft members in opposite directions. 7. The low vibration positive displacement machine according to claim 6, wherein a non-positive displacement machine unit such as a generator and a turbo compressor is driven by two shaft members rotating in opposite directions . In claim 6, the displacement type compressor by two shaft members rotating in opposite directions, displacement pumps, and low vibration displacement, characterized in that a structure for driving the displacement machine units of the Stirling refrigerating machine or the like machine. In claim 8, the two positive displacement machine units driven by the shaft members rotating in opposite directions are connected to the shaft member in a state in which the phases of the periodic changes in the power consumption are substantially equal to each other. Low vibration positive displacement machine. 6. The mechanism according to claim 5, wherein the mechanism for supplying power to the outside through two output shafts rotating in opposite directions is guided by another member to perform reciprocating motion and rotation about an axis in the reciprocating direction. A reciprocating member composed of two arms projecting in opposite directions perpendicular to the reciprocating direction, a guide member as another member for guiding the piston portion of the reciprocating member, and a coaxial rotation axis Two reciprocating members that support relative rotation and change in the direction of the relative rotational axis at positions displaced in the radial direction from the rotational axis while rotating in opposite directions are supported. A shaft member, a final output shaft that extends in the same direction as the movement direction of the reciprocating member and is driven from the two shaft members via a transmission means, a bearing member that supports the rotation of the two shaft members, Bearing member and final output A final bearing frame that supports the reciprocating member is formed as a component, and a closed space is formed adjacent to the reciprocating member to form a working space. The volume of the working space is changed by the pressure of the working fluid, and the reciprocating member is reciprocated. A low-vibration positive displacement machine characterized in that it is a mechanism that drives the two shaft members to rotate in opposite directions .

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