WO2001071188A1

WO2001071188A1 - Displacement type machinery

Info

Publication number: WO2001071188A1
Application number: PCT/JP2000/001649
Authority: WO
Inventors: Isao Hayase; Kunihiko Takao; Takeshi Tsuchiya
Original assignee: Hitachi, Ltd.
Priority date: 2000-03-17
Filing date: 2000-03-17
Publication date: 2001-09-27

Abstract

Displacement type machinery, wherein a second reciprocating mass (26) performing a reciprocating motion in the direction at right angle to the reciprocating motion direction of a first reciprocating mass (A) is added to the first reciprocating mass (A) forming a compression mechanism and a resultant force of these reciprocating motion inertia forces is converted into a load which is constant in size and has a direction rotated together with a driving shaft (2) so as to keep a balance with a centrifugal force of an eccentric mass (2b) fixed to the driving shaft (2), and also a third reciprocating mass (27) reciprocating in the same direction as the second reciprocating mass (26) is added to another position in axial direction so as to also keep a balance with a moment, whereby, because the compression mechanism itself is of a multiple cylinder type and, in addition, reduces a variation in driving torque as a mechanism suitable for two-stage compression, an unbalance caused by an inertia force can be reduced so as to reduce vibration.

Description

Specification

Positive displacement machine

Technical field

The present invention relates to a positive displacement machine, and more particularly to a positive displacement compressor suitable for use in a refrigerating cycle such as a refrigerator and an air conditioner, and an air compressor. Background art

In the case of a reciprocating positive displacement compressor, which is an example of a conventional positive displacement machine, for example, see page 27 and FIG. 0.1 of the document "Hydraulic compressor" (Matsuyoshi Kawahira, published by Japan Refrigeration Association). , Figure 1 0. 2 and FIG. 1 0. as described "3, a cylindrical Suraida a (orbiting piston) is driven revolving with the crankshaft, Suraidaka ^s relatively reciprocally揷入A single piston having a slider guide portion to be reciprocated in a direction perpendicular to the relative reciprocating direction described above,

The opening on the opposite side of the piston bore of the fixed cylinder into which the piston is reciprocally movable is closed by a cylinder head fixed to the fixed cylinder, and the cylinder head is provided with a suction valve and a discharge valve. , And the entire compression mechanism together with the drive motor was floated in a sealed container via a panel or the like. '

Disclosure of the invention

In the above-mentioned reciprocating positive displacement compressor, which is a conventional positive displacement machine, the drive torque fluctuates greatly because a single piston repeatedly alternates between suction, compression and discharge, and unbalance due to the reciprocating motion of the piston. The inertia force ^{s was} generated, causing the compressor to increase the excitation force. In order to prevent the vibration from increasing due to a large excitation force, the compression mechanism and the drive motor must be floated in a sealed container with a panel, which causes the compressor to become larger and increase the cost. Had become. Also, a single relatively large piston is required to replace all required replacement sheets (Rule 26). Since the power is consumed, the deflection from the rotation center of the driving motor to the outermost periphery of the compression mechanism becomes large, which causes the compressor to become large. Furthermore, the compression load due to the gas pressure at the piston head also acts on the sliding part between the slider and the piston before acting on the sliding part between the slider and the crankshaft, increasing friction loss and increasing the efficiency of the compressor. Was causing the decrease. The compression load acting on the bearing due to the gas pressure at the piston head is large even near the top dead center position of the piston where almost no effective compression work is performed, causing the rate of friction loss to increase and reducing the efficiency of the compressor. Had become. A large differential pressure s, which reaches the difference between the compressor suction pressure and the compressor discharge pressure, acts on the seal between the reciprocating biston and the cylinder pore, increasing the internal leakage of working gas and increasing the compressor pressure. Was causing a decrease in efficiency.

Also, the residual gas remaining on the piston head at the top dead center position of Biston re-expanded, which reduced the working gas intake efficiency and reduced the compressor capacity. This decrease was particularly significant when the pressure ratio of the discharge pressure to the suction pressure of the compressor was high.

In addition, the residual gas volume at the top dead center position of the biston increases due to the suction valve attached to the cylinder head, which causes the compressor performance to decrease due to the re-expansion of the residual gas. I was In addition, the working gas is sucked into the working chamber via the suction valve, and the passage resistance is large. Had become.

An object of the present invention is to improve the technical problems of the prior art described above and to provide a positive displacement compressor in which both torque fluctuation and unbalanced inertial force, which are factors of the exciting force, are small and low in vibration. is there.

The above object is a displacement type displacement paper provided with a reciprocating member that is connected to a drive shaft and reciprocates with the rotation of the drive shaft, and the reciprocation causes a change in volume in the working chamber (Rule 26). This is achieved by providing a reciprocating translation member connected to the drive shaft and reciprocating with the rotation of the drive shaft.

Further, the above object is to provide a capacity machine having a reciprocating member connected to a drive shaft and reciprocating with the rotation of the drive shaft, and a volume change occurs in the working chamber due to the reciprocation. This is achieved by providing a reciprocating balance member that is connected and reciprocates with the rotation of the drive and shaft, and a balance weight provided on the drive shaft and based on the reciprocating member and the reciprocal balance member.

In addition, the above object is to provide a cylindrical orbiting member that performs a revolving motion, a drive mechanism that provides the orbital motion to the orbiting member, a fixed frame member that supports the driving mechanism, and a reciprocating motion of the orbiting member. And is supported so as to be able to reciprocate in a direction substantially perpendicular to the axis of the bore, and is operated by reciprocating relative to the revolving member or reciprocating relative to the fixed frame member. A first reciprocating member for causing a volume change in the chamber; and a first reciprocating member driven by the driving mechanism, the first reciprocating member having a phase substantially the same as a reciprocating motion of the revolving member relative to the first reciprocating member. This is achieved by providing a second reciprocating member that reciprocates in a direction substantially orthogonal to the first reciprocating member and does not form a working chamber.

Further, the object is to provide a revolving piston having a revolving motion, a crank pin portion rotatably inserted into the revolving piston, a crankshaft for revolving the revolving piston, and supporting the crankshaft. a fixed frame member, a movable cylinder having at least one fixing piece Sutonboa protruding orthogonally to the swivel Bisutonka ^s orbiting piston bore portion inserted reciprocally and the orbiting piston bore, each fixed Pisutonpoa At least one fixed piston inserted in a reciprocating motion and fixed to the fixed frame member, and at least one end face of the revolving piston bore portion is closed and replaced paper (Rule 26) At least one cylinder head fixed to the fixed frame member; and at least one cylinder head formed by the head end face of each of the turning pistons, the orbiting piston bore portion, and each of the cylinder heads. A second working chamber formed by at least one working chamber, at least one fixed bisdon pore portion, a respective fixed piston, and an outer periphery of the orbiting piston, and the second working chamber with the revolving motion of the orbiting piston. A fluid inflow / outflow mechanism for compressing the fluid by increasing or decreasing the volumes of the first working chamber and the second working chamber; and a second reciprocating member reciprocating in a direction substantially perpendicular to the movable cylinder. Achieved by providing. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a side sectional view showing a positive displacement compressor according to a first embodiment of the present invention, FIG. 2 is a sectional view taken along line II of FIG. 1, and FIG. FIG. 4 is a cross-sectional view of FIG. 1, and FIG. 4 is a view showing the movement of each part when the drive shaft of the configuration of FIG. 2 is rotated by 90 °, and FIG. FIG. 6 is a side sectional view showing a positive displacement compressor according to a second embodiment of the present invention, and FIG. 6 is a sectional view taken along the line III-III of FIG. Best mode for carrying out the invention

A first embodiment of the present invention will be described with reference to FIGS. As shown in FIGS. 1 and 2, a driving mechanism including a revolving piston 1 for revolving motion, a crankshaft 2 for revolving the revolving biston 1 and a driving motor 8, and a fixed support for the driving mechanism A movable cylinder 4 having a frame member 3, a revolving piston pore portion 4 a for reciprocatingly inserting the revolving piston 1, and at least one fixed piston bore portion 4 c projecting orthogonally to the revolving biston bore portion 4 a; At least one of the fixed pistons 5 inserted into the fixed piston bore portion 4c so as to be able to reciprocate and fixed to the fixed frame member 3, and at least one of the end faces of the revolving piston stone portion 4a is closed to fix the fixed frame member. 3 having at least one cylinder head 6, each end face 1 c of the revolving piston 1 and a revolving piston pore 4 a and each replacement sheet (Rule 26) At least one first working chamber 12 is formed by the cylinder head 6, and the outer peripheral cylindrical surface 1 a of each swivel screw-in 1, the respective fixed screw-ton bore 4 c, and the respective fixed piston 5 to form at least one second working chamber 13, and increase or decrease the volume of each of the first working chambers 12 and each of the second working chambers 13 along with the revolving motion of the orbiting piston 1. A fluid inflow / outflow mechanism including a suction port and a discharge port for a fluid to be transferred or compressed is provided. Further, a reciprocating member 26 through a slider 25 through a tip end of a crankpin portion 2a is provided. Is reciprocated in the direction perpendicular to the movable cylinder 4.

Hereinafter, a configuration in which two fixed piston bores and two fixed pistons are provided to form two first working chambers and two second working chambers will be described in detail. In addition, for an example in which one cylinder head is provided to form one first working chamber, and an example in which one fixed biston bore and one fixed biston are provided to form one second working chamber, It is constituted by reading the number of each member.

The revolving piston 1 has an outer peripheral cylindrical surface portion 1a and a central cylindrical hole portion 1b orthogonal to the outer cylindrical surface portion 1a. The crank pin portion 2a of the crank shaft 2 is rotatably inserted into the cylindrical hole portion 1b, and imparts revolving motion to the revolving piston 1. The crankshaft 2 is rotatably supported by a bearing 3 a of a fixed frame 3. The outer peripheral cylindrical surface portion 1a of the revolving piston 1 is inserted into the revolving piston bore portion 4a formed in the movable cylinder 4 in a reciprocating motion force ^s : I dog state. The crank pin portion 2a is inserted into the cylindrical hole portion 1b of the revolving piston 1 through the elongated hole portion 4b formed in the movable cylinder 4. The movable cylinder 4 also has fixed piston pores 4c having smaller inner diameters formed on both sides of the swivel piston 'tonbore 4a, and each of the movable pistons 4 is orthogonally connected to the swivel piston pore 4a. The two fixed piston bores 4 c have two fixed pistons 5 each. Replacement paper (Rule 26) These cylindrical outer peripheral surface portions 5 a are inserted from both sides in a state where relative reciprocating motion is possible, and each fixed piston 5 is fixed to the fixed frame 3. The fixed frame 3 is also fixed so that the two cylinder heads 6 force ^s respectively close the openings at both ends of the orbiting piston bores 4 a of the movable cylinder 4. At this time, the cylinder head 6 and the end of the revolving piston bore 4a are not fixed to each other, but have a small gap so that relative movement between the rainy people is possible. The direction of the plane part 6a of the cylinder head 6 is perpendicular to the center axis of the revolving piston bore part 4a and parallel to the center axis of the fixed piston bore part 4c. Therefore, even if the movable cylinder 4 is guided by the fixed piston 5 and moves in the direction of the center axis of the fixed piston bore portion 4c, the distance between the cylinder head 6 and the end face of the revolving biston pore portion 4a remains unchanged. Although the shell small gap is kept constant, in this embodiment, the seal member 7 is incorporated for airtightness of the minute gap.

In FIG. 3, the slider 25 has a rectangular parallelepiped shape, and has two parallel flat portions 25a and a central cylindrical hole portion 25b orthogonal to the flat portion 25a. The central cylindrical hole 25b is rotatably inserted into the tip of the crankpin 2a. The flat portion 25a is also inserted so as to be capable of a relative reciprocating motion to two parallel flat portions 26a of the reciprocating member 26, and the reciprocating member 26 is a rod portion thereof. 2 6b is guided by the reciprocating motion guide portion 6d of the cylinder head 6 integrally fixed to the fixed frame 3, so that a reciprocating motion force ^{5 in} a direction perpendicular to the reciprocating direction of the movable cylinder 4 is provided. 'Possibly supported.

Returning to FIG. 1, the rotor 8a of the drive motor 8 is mounted on the crankshaft 2, and the stator 8b of the drive motor 8 is fixed to the main chamber 9 together with the fixed frame 3. I have. Openings at both ends of the main chamber 9 are closed by the upper chamber 10 and the lower chamber 11 to form a closed container.

With reference to FIG. 1 and FIG. 4, the above-mentioned configuration allows the crank replacement sheet (Rule 26). When the shaft 2 is rotationally driven by the drive motor 8, the orbiting piston 1 revolves due to the eccentric motion of the crank pin portion 2a. The movement of the swiveling piston 1 in the direction of the piston piston 4 a was not transmitted to the movable cylinder 4 because the rainy person could slide on each other in that direction, and was guided to the movable cylinder 4 by the fixed piston 5. Fixed piston bore 4 Only reciprocating motion in C direction is transmitted. At this time, the swivel piston 1 reciprocates in the swivel piston pore 4a. That is, the head end face 1 c of the orbiting piston turning Bisutonpoa portion 4 a and cylindrical Dae' de of the flat portion 6 _a and two first-stage working chamber being formed with a relatively large maximum volume by the sealing member 7 (First working chamber) 1 2, formed by outer cylindrical surface 1 a of swivel piston 1, fixed piston bore 4 c and fixed piston head 5 b, each having a relatively small maximum volume 2 Four second-stage working chambers (second working chambers) 13, a total of four working chambers, repeatedly increase and decrease in volume as the crankshaft 2 rotates. ,

Also, as shown in FIG. 3, the slider 25 also revolves due to the eccentric motion of the crank pin portion 2a, but the movement of the slider 25 in the plane portion 26a direction is the same in both directions. Are not transmitted to the reciprocating member 26 because they are slidable with each other, and the reciprocating member 26 receives the reciprocating motion guided by the reciprocating guide portion 6d, that is, the reciprocating motion in the direction perpendicular to the movable cylinder 4. Only transmitted. As shown in Fig. 2 and Fig. 4, the working gas (fluid) at the suction pressure is compressed from the suction port 15 of the two places where the suction pipe 14 after branching into two is connected to the main chamber 9 The air flows into the machine, passes through the first-stage suction port (first suction port) 6 b formed in the cylinder head 6, and is sucked into the first-stage working chamber 12. . Since the movable cylinder 4 is guided by the fixed piston 5 and reciprocates in the direction of the piston bore 4c, the flat portion 6a of the cylinder head 6 increases the volume of the first-stage working chamber in the suction stroke. Only in the case of, there is a portion exposed to the first-stage working chamber 12. The suction port 6b is a flat sheet for cylinder head 6 (Rule 26) Formed in such a portion of the surface portion 6a, even if the suction valve is not mounted, the working gas once sucked flows through the suction port 6b during the compression stroke in which the volume of the working chamber 12 decreases. There is no backflow.

The working gas compressed to the intermediate pressure in the first-stage working chamber 12 is supplied to the first-stage discharge port 6c formed in the cylinder head 6 and the discharge valve mounted on the cylinder head 6. After passing through the preload spring 17 and the valve support member 18, the fluid is discharged into a space 19 in a closed container formed by the main chamber 9, the upper chamber 10 and the lower chamber 11. Since the revolving piston 1 reciprocates in the direction of the piston bore 4 a of the movable cylinder 4, the suction stroke in which the volume of the second-stage working chamber 13 increases also on the surface of the outer cylindrical surface 1 a of the revolving piston. There is a part exposed to the working chamber 13 only when A second-stage suction port (second suction port) Id is formed in such a portion on the outer peripheral cylindrical surface 1a of the orbiting piston. The specific shape of the suction port 1d is a groove formed on the outer circumference of the revolving piston 1 so as to reach the elongated hole 4b opening in the revolving piston bore 4a of the movable cylinder 4 '. It is a passage with a shape, and communicates the space 19 in the closed container with the working chamber 13 only when the working chamber 1'3 is in the suction stroke. Therefore, even if the suction valve is not mounted, the working gas once sucked does not flow back to the space 19 in the closed container during the compression stroke.

The working gas at the intermediate pressure in the space 19 passes through the suction port 1 d from the space 19 in the closed container, is further compressed after being sucked into the respective working chambers 13, and is further compressed. Through the second-stage discharge port 5c formed in the valve and the discharge valve 20 and the preload spring 21 and the valve support member 22 incorporated therein. And finally merges into one pipe. The discharge pipe 23 flows out of the compressor at discharge pressure from discharge ports 24 at two places. As described above, the relationship between the conventional piston head and the bore of the cylinder that guides the reciprocating motion is reversed, and instead of the outer cylindrical surface of the piston, the inner cylindrical surface is replaced (Rule 26). It is formed as a fixed piston pore portion 4c of the movable cylinder, and the cylinder has an evening cylindrical surface instead of the inner cylindrical surface of the pore to form a fixed piston head 5b.

According to the first embodiment, since a total of four working chambers can be formed, the compression work per working chamber is reduced, and further, since the phases thereof are shifted from each other, the overall driving torque fluctuation is reduced. It is done. Furthermore, because of the two-stage compression system, the pressure ratio in each working chamber is reduced, which also reduces the drive torque fluctuation itself in each working chamber. As a result, torque fluctuations are greatly uniformed

Next, the principle and mechanism for reducing the inertial force accompanying the reciprocating motion in this embodiment will be described. A second reciprocating member (26) that makes a reciprocating motion in a direction substantially perpendicular to the movable cylinder (4) as the first reciprocating member is provided. By adjusting their mass and amplitude, the resultant force of the respective reciprocating inertial forces can be made a load having a substantially constant magnitude and rotating in the direction substantially at the rotation speed of the crankshaft 2. This load is equivalent to the centrifugal force acting on the eccentric mass, and can be balanced by the counterweight fixed to the crankshaft 2.

That is, for example, if the angular velocity of the crankshaft 2 is ω and the mass of the movable cylinder reciprocating in the X-axis direction is one-sided amplitude, the X-axis positive force F _x is expressed by the following equation. You. F _x = m _l ω ^2- ^ (ω-ή (1) On the other hand, if the mass of the _second reciprocating member reciprocating in the y-axis direction is ₂ and the half amplitude is r ₂ , the y-axis Inertia force: _v is expressed by the following equation.

_{_{F "- m 2 - r 2}} - 2 ■ sin (o) · ή (2) to each other base vector composite force of the inertial force of the perpendicular direction: ^ a magnitude I is the following formula and replacement sheets (Rule 26) Become.

_F \ = (F ^ F-

(3) Now, if r _x = »¾ r ₂ = m .r t, then 'm-r-ω ² = const (4)

Is α, tana = — ^ = tan ((»-(5)

2 ·

From Equations (4) and (5), it can be seen that the combined force of inertia force is a load that rotates at the rotational speed of the crankshaft 2 with a constant magnitude, and the counterweight fixed to the crankshaft 2. It is understood that 2 b can be balanced. From the above formula, for example, a so-called single-cylinder reciprocating machine having only one piston that reciprocates in a cylinder by a drive shaft known as a refrigerator compressor is driven by a drive shaft that drives the piston. By providing a reciprocating balancer that does not contribute to compression and performs a reciprocating motion perpendicular to the direction of the motion of the piston, and by providing a balance weight that matches the reciprocating motion of the drive shaft piston and the inertia force of the reciprocating balancer, the inertia of the piston Vibration due to force can be reduced.

By providing these mechanisms, it is possible to reduce both the drive torque fluctuation and the unbalanced inertia force, which cause the compressor's excitation force, so that a very low-vibration compressor can be provided. It is practically unnecessary to use a vibration-absorbing structure in which the mechanism and the drive motor are floated in a sealed container with a panel, which prevents the compressor from becoming larger and costly due to the adoption of the vibration-proofing structure. In addition, each working chamber only needs to consume a part of the work, so that each working cold is miniaturized, and it is arranged radially around the rotation axis of the driving motor. The whole compressor is reduced in diameter, instead of protruding largely in the radial direction. Replacement form (Rule 26) Next, vibration reduction in the first embodiment of the above-described four cylinders will be described. Assuming that the amount of eccentricity of the crankpin of the crankshaft 2 is, and that the rotational angular velocity is ω, the movable cylinder 4 (the inertial force of the operating cylinder s is the most For the purpose of reducing vibration force)

X = cos (ft). T) (6), and at the same time, the reciprocating member 26, which is the second reciprocating mass (reciprocating balance member), has the y-axis position ¾

A = η. Sin (G)-t) (7)

The mass of the movable cylinder 4 is reciprocated by the reciprocating member, and the mass of 26 is multiplied by ₂ with the equations (6) and (7), differentiated twice with time t, and further multiplied by (-1). The inertial forces F _x , F _{y in} the reciprocating direction of are expressed by the following equations.

F _x = m 'ω ^Λ cos (© t) (8) F .. = · £ ϋ "sin (ω-1) (9)

The relationship between Eqs. (8) and (9) is different from the relationship between Eqs. (1) and (2) given above in that the force is different in that η is common. The results similar to Eqs.) And Eq. (5) can be easily derived, and it can be seen that their vector composite force ^ is a load of constant magnitude and rotating at the crankshaft rotation speed. That is, the balance can be achieved by the balance weight portion 2b of the crankshaft. As a result, in the first embodiment, since both the drive torque fluctuation and the inertial force of the reciprocating motion in an unbalanced manner, which cause the exciting force of the compressor, can be reduced, a very low vibration compressor is provided. The effect is that you can do things. '' Replacement forms (Rule 26) In addition, there is no need to use a panel to float the compression mechanism and the drive motor in a closed container with a vibration isolator, which can prevent the compressor from becoming larger and costly due to the adoption of the vibration isolator. There is. Furthermore, since one compression specifications Kotka per working ^chamber? Small, the working chamber of the first embodiment can be miniaturized as compared with the recip port compressor single cylinder at the same volume for example, the entire compressor is small This has the effect of making it possible. In addition, the pressure of each working chamber directly acts on the head 1c of the revolving piston 1 and the outer cylindrical surface 1a supported by the crank pin 2a, so that the load due to the pressure acts on the head 1c. This has the effect of reducing the sliding parts where friction loss occurs and improving the efficiency of the compressor. Further, in the first-stage working chamber 12 of the first embodiment, despite the relatively large diameter of the revolving piston pore, the maximum attained pressure is an intermediate pressure, so that the head 1C of the revolving piston is located at the head 1C. Applied compressive load s' small. Also, in the second stage of the working chamber 1 3, Razz I contracture in maximum ultimate pressure reaches the discharge pressure, the compression acting on the fixed piston Tonboa ^径Ka? Relatively small because the turning Bisuton outer peripheral cylindrical surface portion 1 a The load is small. That is, in the first embodiment, Ri by the fact that a two-stage compression, the maximum force of the load acting on the sliding portion of the cylindrical hole 1 b and the crank pin portion 2 a of the pivot bis ^tons? Lowered This has the effect of reducing the sliding conditions and improving the reliability.

Furthermore, in the first embodiment, since the suction valve is not required, the passage resistance of the suction passage and the residual gas space in the working chamber can be reduced, and the efficiency and capacity of the compressor are improved. There is.

Also, in the first embodiment, the pressure ratio of each stage is significantly reduced due to the two-stage compression, the adverse effect of the re-expansion of the residual gas in each working chamber is reduced, and the performance of the compressor is improved. This has the effect.

Furthermore, in the first embodiment, the space 19 in the sealed container has an intermediate pressure, and in order to maintain the airtightness of the first-stage working chamber 12, at most the intermediate pressure and the suction pressure are required. Only the differential pressure needs to be sealed, and the airtightness of the second-stage working chamber 13 is maintained. In order to maintain the pressure, only the differential pressure between the discharge pressure and the intermediate pressure needs to be sealed. In other words, the differential pressure to be reduced is smaller than the differential pressure between the discharge pressure and the suction pressure in the case of the conventional single-stage compression, and this has the effect of improving the efficiency and capacity of the compressor by reducing internal leakage. .

5 and 6 show a second embodiment of the present invention. Since the basic structure is similar to that of the first embodiment shown in FIGS. 1 to 4, it will be described mainly on the parts unique to the second embodiment. In the second embodiment, as shown in FIG. 5 and FIG. 6, the reciprocating piston member 27 is fixed to the lower part of the crankshaft 2 ′ via a condro 29 connected by a biston pin 28 ′. The reciprocating member 26 ′ reciprocates in the same direction and in substantially the same phase by the second crankpin member 30 thus formed. That is, the sum of the mass of the reciprocating piston member 27, the mass of the piston pin 28, and a part of the mass of the connecting rod 29 (the mass around the small end) is provided as the third reciprocating mass, A configuration in which the third reciprocating mass and the reciprocating member 26 ′ that is the second reciprocating mass are on the rain side in the axial direction with the movable biston 4 that is the second reciprocating mass interposed therebetween. It has become.

The third reciprocating mass and., When the amount of eccentricity of the second crank pin member 3 0 and r _2, the reciprocating movements by the crank slider mechanism as in the third reciprocating mass to complete sinusoidal motion However, the inertial force in the y-axis direction is roughly expressed by the following equation. F _y = τη ₃ ··· ₂ -ω ² -siai-t) (10) The eccentricity of the crankshaft 2 is set to η as in the first embodiment, and the mass of the reciprocating member 26 ′ is set to _2. If the inertial force in the y-axis direction is approximately

F _y = m ₂ r, ω ² sin (<i)-t) Γ11) Replacement sheet (Rule 26) Incidentally, 'mass "¾ of' the reciprocating member 2 6 young interference smaller than that m ₂ of the first embodiment.

Since the movable piston 4 in the second embodiment is the same as that in the first embodiment, the inertial force F _{x in the} X-axis direction is expressed by the following equation (8).

As shown in FIG. 5, when the axial distance between the movable piston 4 and the reciprocating member 26 ′ is defined as the axial distance between the movable piston 4 and the reciprocating biston member 27, the second distance is obtained. In the configuration of the embodiment of

F _y + F _y = F _X (12)

F _y -L ₂ = F _y -L _x (13) A combination of m ₃ and r ₂ that satisfies both equations at the same time can be selected. That is, in the configuration of the second embodiment, inertial force F _y + F _y inertia mosquito ^ and y-axis direction of the X-axis direction is vector synthesized as a force acting in the axial direction of the same plane, the size Is constant and the load rotates at the rotation speed of the crankshaft 2 '. '' Therefore, not only the inertia force in the X-axis direction and the y-axis direction, but also the X-axis and y-axis inertia forces are obtained by the balance weight 31 attached to the crankshaft balance weight part 2 b and the drive motor rotor part 8a. The moment generated by the inertial force around the axis and y-axis can be almost completely balanced. In the structure of the first embodiment] ^, the inertia force in the X-axis direction and the y-axis direction can be completely balanced, and the moment generated by the inertia force around the X-axis and y-axis is completely It is not possible to let them know.

As described above, the inertia balance can be more completely achieved in the second embodiment, so that there is an effect that a positive displacement compressor with lower vibration can be provided as compared with the first embodiment. The other effects of the first embodiment can be similarly obtained in the second embodiment.

Replacement form (Rule 26) The third reciprocating mass in the second embodiment is the second crank pin. The member 30, the connector 29, the piston pin 28, the reciprocating piston member 27, and the reciprocating piston member 2 The reciprocating motion is given by a “crank-slider mechanism” consisting of a cylinder member 32 that guides the reciprocating motion of the reciprocating motion. A reciprocating motion may be provided using the "Scotch yoke mechanism" that provides motion. Conversely, in the first and second embodiments, the reciprocating motion is given to the second reciprocating mass by the “sketch choke mechanism”, but the reciprocating motion is given to the “crank-slider mechanism”. Even if the structure is changed, the effects of the invention described above can be obtained almost in the same manner. ,

According to the first and second embodiments described above, two first working chambers and two working chambers are respectively provided inside the swivel piston bore of the movable cylinder and inside the fixed piston bore. A total of two working chambers can be formed. 'Moreover, Ki they ^force? Turning to repeat the offset change in the volume of the bis tons revolving nine 0 ° with the motion transfer, de be be made by dispersing the four overall workload in each working chamber, In addition to the reduction of the driving torque fluctuation of each working chamber, the driving torque fluctuations having a phase shift are superimposed and the torque fluctuation force ^{s is} made uniform. In particular, in the case of a two-stage compression system in which the first compression is performed in the first working chamber and then guided to the second working chamber to perform the second compression, the individual compression in each working chamber is considered. Since the drive torque fluctuation itself becomes smaller as the pressure ratio in each working chamber becomes smaller, the torque fluctuation becomes more uniform. ·

The first working chamber and the second working chamber are sealed spaces formed by inner peripheral wall surfaces that are constituted by both ends or the outer periphery of the swivel piston, and the pressure of each working chamber is directly applied to both ends of the swivel piston. And the outer periphery, and then the turning piston is directly supported by the sliding load of the crankpin of the crankshaft. In other words, the conventional technology causes a large sliding load to act and increases the friction loss. The number of sliding portions corresponding to the sliding portion between the slider and the piston, which has been reduced, is reduced, and the efficiency of the compressor can be improved. In addition, the crankshaft always performs effective compression work for the other working chamber even if it does not perform compression work for one working chamber at the top dead center, and friction due to bearing load Losses always occur for a certain amount of useful work, and the ratio of friction loss to useful work can be reduced and efficiency can be improved.

When each working chamber changes its volume, the movable cylinder reciprocates with respect to the cylinder head, and the orbiting piston reciprocates with respect to the movable cylinder. The cylinder head forming the first working chamber in the swiveling piston port of the movable cylinder and the side of the swiveling piston forming the second working chamber in the fixed piston bore have the respective working chamber volumes. It is possible to open the suction port exposed to the working chamber only while the pressure increases, eliminating the need for the suction valve that caused the increase in the passage resistance.

In addition, in the conventional structure using a suction valve, a residual gas space is created in a part other than the lift restriction part of the suction valve and the part on the cylinder head surface where the suction valve is mounted, whereas there is no suction valve. The structure enables a design to reduce the residual gas volume. , _:

Next, two types of bore cross-sectional areas are provided, and the fluid that has completed the first stage compression in the first working chamber with a large bore cross-sectional area is guided to the second working chamber with a small bore cross-sectional area. A structure that performs second-stage compression can be provided. Therefore, even if the cross-sectional area of the bore of the orbiting piston is relatively large, the maximum working pressure is still the intermediate pressure by using the first working chamber there for the first stage compression. However, the maximum pressure in the fixed piston bore reaches the discharge pressure of the compressor due to the second stage compression, but its cross-sectional area becomes smaller. In other words, the compressive load acting on the revolving piston head and side faces is smaller than the conventional compressive load acting on the piston head.

In the case of two-stage compression, the pressure inside the airtight container of the compressor must be changed to the first-stage replacement paper (Rule 26). The differential pressure to be sealed in the first working chamber of the first stage is the differential pressure between the suction pressure of the compressor and the intermediate pressure, and the second pressure of the second stage is The differential pressure to be sealed in the working chamber is the differential pressure between the intermediate pressure and the discharge pressure of the compressor, and both are smaller than the differential pressure between the suction pressure and the discharge pressure, which is the conventional differential pressure to be sealed. Leakage is reduced. Also, in a structure that performs two-stage compression, the pressure ratio in each stage is smaller than the pressure ratio when compression is completed in one stage, so the influence of the re-expansion of residual gas in each working chamber ^s can be reduced, and the capacity of the compressor can be improved. Next, the component configuration of the compressor and the shape and function of each component are not much different from those of the components of the conventional reciprocating compressor, and conventional equipment and processing for efficient cylindrical and planar processing are efficient. Since technology can be used, low-cost production is possible.

As described above, according to the present invention, it is possible to provide both a low-vibration positive displacement machine by reducing both the drive torque fluctuation and the balance inertia force.

Replacement form (Rule 26)

Claims

The scope of the claims

1. In a positive displacement machine provided with a reciprocating member that is connected to a drive shaft and reciprocates with the rotation of the drive shaft, and the reciprocating motion causes a change in the volume of the working chamber, this is connected to the drive shaft. A positive displacement machine equipped with a reciprocating balance member that reciprocates as the drive shaft rotates. '

2. A positive displacement machine having a reciprocating member that is connected to a drive shaft and reciprocates with the rotation of the drive shaft, and the reciprocating motion causes a volume change in the working chamber. A positive displacement machine comprising: a reciprocating balance member that reciprocates with rotation of a shaft; and a balance weight provided on the drive shaft and based on the reciprocating member and the reciprocating translation member.

3. A cylindrical revolving member for revolving motion, a drive mechanism for revolving the revolving motion member, a fixed frame member for supporting the driving mechanism, and the revolving member inserted reciprocally. A reciprocating motion in a direction substantially orthogonal to the axis of the bore portion, and a change in volume in the working chamber due to reciprocating motion relative to the revolving member or reciprocating motion relative to the fixed frame member. A first reciprocating member to be generated; driven by the drive mechanism; and substantially the same as the first reciprocating member in substantially the same phase as the reciprocating movement of the revolving member relative to the first reciprocating member. A positive displacement machine comprising: a second reciprocating member that reciprocates in an orthogonal direction and does not form a working chamber. -4, a cylindrical orbiting member for revolving motion, a drive mechanism for providing orbital motion to the orbiting member, a fixed frame member for supporting the driving mechanism, and the orbiting member inserted reciprocally. And is supported so as to be able to reciprocate in a direction substantially orthogonal to the axis of the bore portion, and the volume of the working chamber is changed by reciprocating motion relative to the revolving member or reciprocating motion with respect to the fixed frame member. A first reciprocating member for generating the following reciprocating motion; and a sheet having substantially the same phase as a reciprocating motion of the revolving member relative to the first reciprocating member driven by the driving mechanism (Rule 26) A first reciprocating member, a second reciprocating member that reciprocates in each of the orthogonal directions B, and a second reciprocating member that is driven by the driving mechanism; The first reciprocating member having substantially the same phase as the reciprocating motion, and a third reciprocating member reciprocating in a direction substantially orthogonal to the first reciprocating member. The second reciprocating member and the third reciprocating member. Is a positive displacement machine arranged in the axial direction with the first reciprocating member interposed therebetween.

5. A revolving piston that revolves, a crankshaft that revolves the revolving piston with a crankpin that is rotatably inserted into the revolving piston, a fixed frame member that supports the crankshaft, A rotating piston bore portion inserted reciprocally; a movable cylinder having at least one fixed piston bore portion projecting perpendicular to the rotating piston bore portion; and a fixed piston bore portion. At least one fixed piston inserted reciprocally into the fixed frame member and at least one cylinder fixed to the fixed frame member by closing at least one end face of the orbiting piston bore portion. A head, an end face of each head of the orbiting piston, and the orbiting piston pore And at least one first working chamber formed by at least one cylinder head, at least one first piston formed by at least one fixed piston bore, at least one fixed piston, and at least one outer periphery of the orbiting piston. A second working chamber;-increasing or decreasing the volumes of the first working chamber and the second working chamber in accordance with the revolving motion of the orbiting piston to compress the fluid;

And a second reciprocating member reciprocating in a direction substantially perpendicular to the movable cylinder.

6. A revolving piston that revolves, a crankshaft that revolves the revolving piston with a crankpin that is rotatably inserted into the revolving piston, a fixed frame member that supports the crankshaft, Swivel piston bore where the piston can be reciprocated and this swivel replacement sheet (Rule 26) A movable cylinder having at least one fixed piston bore protruding orthogonally to the stone bore, at least one fixed piston inserted reciprocally into each fixed piston bore and fixed to the fixed frame member; At least one cylinder head which closes at least one end face of the revolving piston bore and is fixed to the fixed frame member; a head end face of the revolving piston, the revolving piston bore and the respective cylinder head; And at least one second working chamber formed with at least one fixed piston hole portion, at least one fixed piston, and at least one evening of the orbiting piston. And the volumes of the first working chamber and the second working chamber due to the revolving motion of the orbiting piston. A fluid reciprocating mechanism that reciprocates in a direction substantially perpendicular to the movable cylinder; a reciprocating member that reciprocates in a direction substantially perpendicular to the movable cylinder; a reciprocating member that reciprocates in a direction substantially perpendicular to the movable cylinder; A positive displacement compressor comprising: a third reciprocating member disposed at a position sandwiching the first reciprocating member in an axial direction together with a second reciprocating member.

7. The volume in Claim 5 or 6, wherein two fixed piston bores, two fixed pistons, and two cylinder heads are provided, and two first working chambers and two second working chambers are formed. Shape compressor.

8. In any one of claims 3 to 5, the fluid inflow / outflow mechanism is provided in each cylinder head, and the first inflow / outflow mechanism is provided in accordance with the revolving motion of the swivel piston. Only while the volume of the first working chamber increases, at least one first suction port communicating with the respective first working chamber, and the volume of each second working chamber provided in the swivel piston. A positive displacement compressor comprising at least one second suction port in communication with each second working chamber only while increasing.

9. The positive displacement compressor according to claim 8, wherein each discharge port is equipped with a discharge valve that opens and closes according to a pressure difference between the front and rear of the fluid.

10. The movable cylinder according to any one of claims 5 to 9, wherein the movable cylinder includes a rotation replacement sheet (Rule 26). A positive displacement compressor fitted with a seal member that seals the gap between each end face of the rotating biston bore and the cylinder head.

11. In any one of claims 5 to 10, wherein the orbiting piston has a cross-sectional area larger than a cross-sectional area of each fixed piston, and fluid flows in each of the first working chambers. A positive displacement compressor that performs the first stage compression, and then leads to each second working chamber to perform the second stage compression.

Replacement form (Rule 26)