JPH0925882A - Fluid machinery with trochoid tooth form - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate unbalance force generated due to the asymmetric structure of a rotating system without increasing the weight of a machine, make the machine compact and lightweight, and to attain high speed and large capacity by balancing the unbalance force of a first and a second inner rotor parts, a rotating suction hole plate and a rotating delivery hole plate. SOLUTION: A camshaft 3 is provided with a first and a second cams 31, 32 with the phase difference of 180 deg. along an axial direction. A first and a second inner rotors 1a, 1b are fitted to the first and second cams 31, 32 in such a way as to be revolvable and autorotatable, and the first and second inner rotors 1a, 1b are engaged with a first and a second outer rotors 2a, 2b. Further, a rotating suction hole plate 7 with a suction hole, and a rotating delivery hole plate 6 with a delivery hole are fitted to the camshaft 3 with the phase difference of 180 deg. and rotated synchronously with the camshaft 3. Unbalance force is dynamically balanced by the first and second inner rotors 1a, 1b, the rotating suction hole plate 7 and the rotating delivery hole plate 6. High speed and large capacity can thereby be realized.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention has a pair of trochoid tooth-shaped teeth in which a rotary disk having a suction hole and a rotary disk having a discharge hole are arranged side by side in an axial direction, and the volume changes between the rotary disks by rotation. TECHNICAL FIELD The present invention relates to a fluid machine having a trochoidal tooth profile in which a rotor provided with a rotor is interposed, and a fluid is pressure-fed or rotational force is transmitted through the fluid by a change in volume of the rotor.

[0002]

2. Description of the Related Art In a rotary fluid machine for pumping a fluid by rotating a pair of rotors, a trochoid compressor equipped with a rotor having a trochoid tooth profile has recently been used as a compressor for pumping gas and a pump for pumping liquid. Has been used a lot.

A trochoidal tooth profile fluid machine for fluid pumping provided with a rotor having this trochoidal tooth profile combines an inner rotor having a trochoidal tooth profile and an outer rotor, and an inner rotor that is revolvably and self-rotatably fitted to a cam shaft is provided in the cam. The inner and outer rotors are rotatably driven, and a rotary disk with suction holes and a rotary disk with discharge holes are arranged in parallel on both sides of the inner and outer rotor shaft ends, and the fluid sucked from the suction holes is stored between the trochoid teeth of the inner rotor and the outer rotor. It is configured to be introduced into the inside and pressurize the fluid by the volume change (reduction) due to the relative rotation of both rotors, and deliver the fluid from the discharge hole to the destination.

In the above trochoid tooth profile fluid machine, the cam shaft and the inner rotor are asymmetric with respect to the axial center. The unbalanced weight due to this asymmetrical structure occupies a large weight ratio with respect to the total weight of the fluid machine, and therefore excessive vibration and noise are generated during high-speed operation of the fluid machine, and the increase in capacity due to high speed is hindered. As a result, the durability is lowered.

In order to solve the problem caused by the unbalanced weight, a suction side turntable with suction holes and a discharge side turntable with discharge holes which rotate on both sides of the inner rotor are used.
A technique for attaching a balancing weight (balancer) that generates a force for canceling the unbalanced force due to the unbalanced weight to these rotary disks has been proposed by the applicants of the present application as a prior application technique.

[0006]

However, in the means for providing the balancing weight provided by the above-mentioned prior art by using the suction / discharge rotating disk, it is possible to reduce or cancel the unbalanced force. However, as described above, in the trochoidal tooth profile fluid machine, since the proportion of the unbalanced weight in the entire machine is large, the weight of the balancer is inevitably large, and the machine weight increases and the machine body The size of the fluid machine is increased, which is an obstacle to high rotation and large capacity of the fluid machine.

The object of the invention is to increase the weight of the machine without
Alternatively, by minimizing the increase in weight and eliminating the unbalanced force associated with the asymmetrical structure of the rotary system, a fluid machine equipped with a trochoid tooth profile that has been made compact and lightweight to achieve high speed and large capacity Is to provide.

[0008]

SUMMARY OF THE INVENTION The present invention relates to a fluid machine provided with a trochoidal tooth profile in which an inner rotor and an outer rotor having a trochoidal tooth profile are combined and a fluid is pressure-fed by a change in meshing volume. 1
The first and second cams having a phase of 80 ° are provided, and the first and second cams are provided.
The first and second inner rotors are fitted to the second cam so as to be able to revolve and rotate, and the first and second inner rotors are fitted to the first and second inner rotors.
A rotary suction hole disk having a suction hole and a rotary discharge hole disk having a discharge hole, which are engaged with the second outer rotor, are attached to the cam shaft at a phase of 180 ° with respect to each other, and are rotated synchronously with the cam shaft. The gist is that the unbalanced force is dynamically balanced by the inner rotor, the rotary suction hole plate, and the rotary discharge hole plate.

That is, according to a first aspect of the present invention, an inner rotor having trochoidal tooth-shaped outer teeth and revolvingly and revolvably fitted to a cam shaft is meshed with an outer rotor having trochoidal tooth-shaped inner teeth, In a trochoidal fluid machine configured to deliver fluid from an inlet to an outlet by a change in meshing volume due to relative rotation of both rotors, the camshaft has a phase of 180 ° in the circumferential direction. A first cam and a second cam are provided, and the inner rotor is axially divided into a first inner rotor and a second inner rotor, the first inner rotor is the first cam, and the second inner rotor is the second cam. Respectively, and the outer rotor is axially divided into a first outer rotor and a second outer rotor, and inner teeth of the outer rotor and the first inner rotor and the second outer rotor are fitted to each other. The inner rotor is fitted in this order, and a rotary suction hole plate having a working fluid suction hole and an unbalanced weight and a rotation discharge hole plate having a working fluid discharge hole and an unbalanced weight are provided on the camshaft. So that both unbalanced weights are 180 ° in phase with each other,
And a trochoidal tooth profile, which is rotatably mounted in synchronization with the cam shaft, and is configured to balance the unbalanced forces of the first and second inner rotor portions, and the rotary suction hole plate and the rotary discharge hole plate. It is in the equipped fluid machine.

In addition to the first means, the second means is fitted between the first inner rotor and the second inner rotor on the cam shaft so as to be rotatable in synchronization therewith, and the first means is also provided. The meshing volume of the inner rotor and the first outer rotor and the meshing volume of the second inner rotor and the second outer rotor are communicated with each other through a rotary communication hole plate.

The third means is that the first outer rotor and the second outer rotor in the first and second means are fixed to the housing together with the coupling ring interposed between the two rotors. is there.

Further, a fourth means is a second rotary shaft in which the first outer rotor, the second outer rotor and the coupling ring in the first and second means are provided on the opposite side in the axial direction of the cam shaft. And is made rotatable with the second rotating shaft.

In the fluid machine provided with the trochoidal tooth profile, like the third means, the first and second outer rotors and the coupling ring are fixed to the housing. It is suitable for a pump for doing so, and the fourth means for rotating the first and second outer rotors and the coupling ring to form the output end is suitable as a fluid transmission.

Further, in the fluid machine, preferably, the rotary communication hole plate is located at an inner peripheral portion of the coupling ring and is attached to the cam shaft, and is always on the first inner side, the outer rotor side and the second inner side, the outer rotor. It is configured to communicate between the side meshing volumes.

Further, in the fluid machine, preferably, the first and the first members mounted on the cam shaft in a phase of 180 °.
The second inner rotor has the same shape, and the suction hole of the rotary suction hole plate and the discharge hole of the rotary discharge hole plate are provided so as to be deviated from the axis of rotation and have a phase of 180 ° for rotation. The suction hole plate and the rotary discharge hole plate are symmetrical with respect to the rotation axis, and the unbalanced forces of the two rotary plates are
The unbalanced force of the second inner rotor, that is, the inertia couple, acts in the opposite direction to completely cancel it.

Since the present invention is constructed as described above, according to the first, second and third means, the first and second inner rotors are in phase with each other by 180 ° due to the rotation of the camshaft. The rollers revolve orbit and rotate, but the inertial forces of both rollers are canceled by the rotation of both rollers in the phase of 180 °. Further, the rotary suction hole plate and the rotary discharge hole plate also rotate with a phase of 180 ° with respect to each other, and the inertial forces of both are canceled out.

On the other hand, the inertia couples of both rollers remain, but the inertia couples of the rotary suction hole plate and the rotary discharge hole plate which are arranged in front of and behind both rollers and rotate with a phase of 180 °. Since it acts in the direction opposite to the inertial couple of both rollers, this also cancels out. This provides a complete dynamic balance of the fluid machine.

That is, the inner rotor is divided into two in the axial direction and arranged with a rotational phase of 180 °, and the rotary suction hole disk and the rotary discharge hole disk are arranged with a 180 ° rotational phase. Using the unbalanced force due to the original asymmetric structure of the rotary suction hole plate and the rotary discharge hole plate, it is only necessary to properly set the structure and arrangement of the functional members of the fluid machine itself. The complete dynamic balance of the machine can be achieved without any reduction.

According to the fourth means, the first and second outer rotors are rotated together with the coupling ring, the output shaft is connected to this, and the amount of fluid operating between the inner rotor and the outer rotor is controlled. The number of revolutions of the output shaft can be controlled, and as described above, a variable speed fluid transmission having complete dynamic balancing can be obtained.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to FIGS. However, unless otherwise specified, the dimensions, materials, shapes, relative positions, etc. of the components described in this embodiment are not intended to limit the scope of the present invention thereto, but merely illustrative examples. Nothing more.

FIG. 1 is a cross-sectional view of a compressor having a trochoidal tooth profile according to an embodiment of the present invention taken along the center line of the rotation axis, FIG. 2 is an external view of a cam shaft of the compressor, and FIG. 3 is a view of the compressor. FIG. 4 is a front external view of the inner rotor and the outer rotor, illustrating the operation of the rotary communication hole plate.

In FIGS. 1 and 2, reference numeral 3 denotes a cam shaft rotatably driven by a drive source such as an electric motor and an engine. The cam shaft 3 has a first cam 31 and a second cam 32 in the axial direction.
The eccentric cams are arranged in parallel at a phase of 180 °.

A first inner rotor 1a is rotatably fitted to the first cam 31 of the cam shaft 3, and a second inner rotor 1a having the same shape as the first inner rotor 1a is rotatably fitted to the second cam 32. The outer peripheries of the inner rotors 1a and 1b are formed with known trochoid external teeth (cycloid teeth) 61 as shown in FIG. 4 (A).
The inner rotors 1a and 1b have the rotational axis 3a as described above.
The first and second cams 3 which are eccentric with respect to each other by 180 ° in phase
By being rotatably fitted to the camshafts 1, 32, the camshaft 3
Of the cam shaft center 3a by the rotation of the
The cam shaft center 31a and the second cam shaft center 32a rotate on their own axes.

Reference numeral 2a is a first outer rotor, 2b is a second outer rotor having the same shape as the first outer rotor, and FIG.
As shown in (B), it has a trochoidal internal tooth 62, the rotors 2a, 2b have one more tooth than the inner rotors 1a, 1b, and the outer rotor 2a is installed between them. , 2b are integrally joined by bolts 41 to a joint ring 4 having an outer diameter slightly larger than the root diameter of each tooth.

The first inner rotor 1a and the first outer rotor 2a, and the second inner rotor 1b and the second outer rotor 2b are the known trochoid teeth 62 as described above.
(Cycloid teeth) meshing with the camshaft 3
By being revolved or revolving by, the volume changes and the fluid is compressed.

Reference numeral 11 denotes a rotary communication hole plate rotatably fitted to the inner circumference of the coupling ring 4, and the inner circumference of the rotary communication hole plate 11 is fitted to the notch 3a at the center of the camshaft 3. The first and second inner rotors 1a, 1b and the first and second outer rotors 2a,
It is rotatable with the cam shaft 3 while being in contact with the side surface of 2b.

Reference numeral 5 denotes a housing in which the first and second outer rotors 2a and 2b and the coupling ring 4 are incorporated. In the case of a gas compressor, a liquid pressure pump, etc., the first and second outer rotors 2a, 2b and the coupling ring 4 are fixed to the housing 75 and integrated to form a stationary body. Further, in the case of a fluid transmission, as will be described later, the first and second outer rotors 2a and 2b and the coupling ring 4 are a rotating body that rotates in the housing 5 by integrating three members.

Reference numeral 7 is a rotary suction hole plate, 6 is a rotary discharge hole plate, and the rotary suction hole plate 7 and the rotary discharge hole plate 6 are fitted in the notches 3c and 3b of the cam shaft 3, respectively, and the cam shaft 3 The first and second inner rotors 1a and 1b and the first and second outer rotors 2a and 2b rotate in contact with the side surfaces of the first and second inner rotors 1a and 1b. The rotary suction hole plate 7 and the rotary discharge hole plate 6 may be assembled by replacing each other depending on the rotation direction of the cam shaft 3.

3A and 3C are plan views of the rotary suction hole plate 7 and the rotary discharge hole plate 6. FIG.
The rotary suction hole plate 7 shown in (C) is formed with a groove 72 on the outer circumference and a discharge hole 71 having an inner bottom with a magenta shape. As shown in FIG. 2, the outer peripheral groove 72 is communicated with the suction port 10 of the housing, while the outer peripheral groove 72 is also communicated with the beaded discharge hole 71, so that the outer peripheral groove 72 is connected to the shaft center 3a. It has an asymmetrical weight structure.

As a result, the fluid from the suction port 10 is sucked into the meshing volume portion of the second outer rotor 2b and the second inner rotor 1b through the groove 72 and the discharge hole 71 of the rotary suction hole plate 7.

The rotary discharge hole plate 6 shown in FIG.
Similarly to the rotary suction hole plate 7, an axial center provided with an outer peripheral groove 62 communicating with the discharge port 9 of the housing 5 and a discharge hole 61 having a beaded bottom communicating with the groove 72. Three
The shape is asymmetric with respect to a. As a result, the fluid discharged from the meshing volume of the first inner rotor 1a and the second outer rotor 2a is discharged into the discharge hole 61 and the outer peripheral groove 62.
After that, it is discharged to the discharge port 9 of the housing 5.

Further, the rotary suction hole plate 7 and the rotary discharge hole plate 6 are symmetrical with respect to the shaft center 3a, in which the suction holes 71 and the discharge holes 61 are provided at a phase of 180 ° with each other. . As a result, the rotary suction hole plate 7 and the rotary discharge hole plate 6 are unbalanced by weight, that is, the suction hole 7
1 and the portion on the symmetrical side of the discharge hole 61 are attached to the cam shaft 3 so that the phases thereof are 180 ° relative to each other.

Further, the unbalanced weight portion of the rotary suction hole plate 7 and the unbalanced weight side of the second inner rotor 1b and the second cam 32, that is, the eccentric side, are 180 ° in phase, and the rotary discharge hole plate 6 is provided.
The above-mentioned unbalanced weight portion and the unbalanced weight side, that is, the eccentric side of the first inner rotor 1a and the first cam 31 are arranged at a phase of 180 °.

Therefore, the first and second inner rotors 1a,
180 of the unbalanced weight of the 1b and the first and second cams 31 and 32 and the rotary suction hole plate 7 and the rotary discharge hole plate 6 as described above.
By the arrangement in ° phase, the dynamic balance of the rotating system can be perfectly achieved.

FIG. 3B shows a front view of the rotary communication hole plate 11. Corresponding to the suction holes 71 of the rotary suction hole plate 7 and the discharge holes 61 of the rotary discharge hole plate 6 on both sides of the rotary communication hole plate 11, there are discharge passage holes 611 in the shape of bottomed beads.
612 and the suction passages 711, 712 on the back side thereof
The discharge passage holes 611 and 61 are provided with a phase difference of 80 °.
2 are communicated with each other through a communication passage 613, and each suction passage hole 711
And 712 are connected by a communication passage 713.

Therefore, as described above, the first and second inner rotors 1a and 1b which are respectively revolved and rotated by being fitted to the pair of cams of the first cam 31 and the second cam 32, which are formed in the phase of 180 °, respectively. The meshing volume of the first and second outer rotors 2a, 2b meshing with the inner rotors 1a, 1b by trochoidal teeth allows the rotary communication hole plate 11 to always communicate with each other even while the camshaft 3 is rotating. Reference numerals 8 and 8 denote bearings that support the cam shaft 3 on the housing 5.

During operation of the rotary compressor having the trochoidal tooth profile configured as described above, the rotation of the cam shaft 3 causes the first inner rotor 1a and the second inner rotor 1b to form a phase of 180 ° with each other, and the cam shaft center 3a. Centers 31a, 3 of the first cam 31 and the second cam 32 while revolving above
The first outer rotor 2a and the second outer rotor 2 which rotate on the 2a and are fixed to the outer teeth 61 and the housing 5.
The volume formed between the inner teeth 62 of b is changed.

On the other hand, the rotary suction hole plate 7 and the rotary discharge hole plate 6 which are fixed to the cam shaft 3 are also synchronized with the cam shaft 3 and have a mutual position of 1.
The fluid rotates by a phase of 80 °, sucks the fluid into the volume through the suction hole 71 in the vicinity of the maximum volume, compresses the fluid, and compresses the compressed fluid in the discharge hole 61 in the vicinity of the minimum volume. Is discharged.

During the operation, the first cam 31, the first inner rotor 1a fitted to the first cam 31, and the second cam 32 are provided.
And the second inner rotor 1b fitted to the
Rotate in a phase of 80 °.

Therefore, the inertial force between the first inner rotor 1a side and the second inner rotor 1b side is completely canceled, but the inertial couple remains.

On the other hand, due to the eccentric arrangement of the suction hole 71 of the rotary suction hole plate 7 and the discharge hole 61 of the rotary discharge hole plate 6, the unbalanced weight part on the rotary suction hole plate 7 side is 18 and the second inner rotor 1b side.
While forming a phase of 0 °, the unbalanced weight portion on the side of the rotary discharge hole 6 rotates in a phase of 180 ° with the side of the first inner rotor 1a.

Therefore, by the rotation of the rotary suction hole plate 7 and the rotary discharge hole plate 6, the inertia couple remaining on the inner rotor side is canceled. This completely counteracts all unbalanced forces, resulting in perfect dynamic balance.

In the above operation, when the first and second inner rotors 1a and 1b rotate at high speed, the inner rotor 1
a and 1b outer teeth 61 and the first and second outer rotors 2a and 2b
The flow of the fluid passing through the meshing volume formed between the inner teeth 62 and the inner teeth 62 is communicated between the first and second rotors through the rotary communication hole plate 11 that rotates together with the cam shaft 3. Flows in the same direction through the hole plate 11.

Further, since the first and second inner rotors 1a and 1b revolve and rotate about the phase of 180 ° with respect to each other, they both suction and discharge the communication holes 711 of the rotary communication hole plate 11.
It rotates in a state where it is always communicated through 712, 611, 612 and communication passages 713, 613.

Therefore, the flow of the fluid in the axial direction at the time of the operation is as follows: the suction port 10 → the rotary suction hole plate 7 → the meshing volume between the second inner rotor 1b and the second outer rotor 2b →
The rotary communication hole plate 11 → the meshing volume of the first inner rotor 1a and the first outer rotor 2a → the rotary discharge hole plate 6 → the discharge port 9 becomes a unidirectional flow suitable for high-speed rotation.

The rotary suction hole plate 7 and the rotary discharge hole plate 6
Has the function of switching between suction and discharge of fluid as described above, and the side surfaces of both the plates 7 and 6 also perform a hermetic sealing action with the side surfaces of the outer rotors 2a and 2b and the inner rotors 1a and 1b. Therefore, leakage of fluid from the side portions of both rotors is prevented.

A second embodiment of the present invention is shown in FIGS. In this embodiment, a fluid machine having trochoidal teeth is applied to a fluid transmission, and in FIGS. 5 and 6, a coupling member 12 is fixed to an end portion of the first outer rotor 2a, and the coupling member 12 has a first coupling member. Two rotating shafts are fixed. Thus, the first outer rotor 2a, the second outer rotor 2b, the coupling ring 4 that couples both rotors, and the coupling member 12
The second rotary shaft 13 and the second rotary shaft 13 can rotate together in the housings 5 and 5a.

In FIGS. 5 and 6, when the cam shaft 3 is rotated, the fluid introduced from the suction hole 10 causes the rotation suction hole plate 75 → the second inner rotor 1b and the second outer rotor 2 to rotate.
The mesh volume with b → the rotary communication hole plate 11 → the mesh volume with the first inner rotor 1a and the first outer rotor 2a → the rotary discharge hole plate 65 → the discharge port 9, but the outer rotors 2a, 2b side is rotatable. Since the outer rotor side is driven by the fluid, the first and second outer rotors 2a and 2b, the coupling ring 4, the coupling member 12, and the second rotary shaft 13 serve as driven bodies, and the second rotary shaft 13 Rotational force can be extracted from the shaft end.

In this case, an external pipe is provided between the suction port 10 and the discharge port 9, and a flow rate adjusting valve is provided in this pipe to adjust the amount of fluid flowing through the flow path inside the fluid machine. The rotation speed output from the second rotation shaft 13 can be changed.

Further, the first inner rotor 1a and the second inner rotor 1b, and the rotary discharge hole plate 6 and the rotary suction hole plate 7 are arranged so as to have a phase of 180 ° with each other to cancel the unbalanced force. The same as the first embodiment.

The structure other than the above is the same as that of the first embodiment shown in FIGS. 1 to 4, and the same members are designated by the same reference numerals.

[0052]

The present invention is configured as described above.
According to the invention of claims 1 to 3, in the fluid machine having the trochoidal tooth profile, the cam shaft is provided with the first and second cams having a phase of 180 ° along the axial direction, and the first and second cams are provided. The first and second inner rotors are fitted to each other so that they can revolve and rotate, and the first and second inner rotors are meshed with the first and second outer rotors, and the rotation has a suction hole plate having a suction hole and a rotation hole having a discharge hole. Discharge perforations with cam shaft as one
The inner rotor is mounted in a phase of 80 ° and rotated synchronously with the cam shaft, and the first and second inner rotors, the rotary suction hole plate, and the rotary discharge hole plate are configured to dynamically balance the unbalanced force. The rotary suction hole plate and the rotary discharge hole plate are arranged with a 180 ° rotation phase, and the rotary suction hole plate and the rotary discharge hole plate are arranged with a 180 ° rotation phase. Utilizing the unbalanced force due to the original asymmetric structure of the drilling hole, only by appropriately setting the structure and arrangement of the functional members of the fluid machine itself, without increasing the weight or lowering the function of the fluid machine, A perfect dynamic balance of the machine can be achieved.

As a result, it is possible to obtain a trochoid tooth type fluid machine in which the dynamic balance is completely achieved by the small and lightweight structure, and the high speed and large capacity can be realized.

According to the fourth aspect of the invention, the two outer rotors are rotated together with the coupling ring, the output shaft is connected to the two outer rotors, and the amount of the fluid operating between the inner rotor and the outer rotor is controlled to output the output. The number of rotations of the shaft can be controlled, and as described above, it is possible to obtain a fluid transmission of a variable speed which is perfectly dynamic balanced.

[Brief description of drawings]

FIG. 1 is a sectional view taken along the axis of rotation of a fluid compressor having a trochoidal tooth profile according to a first embodiment of the present invention.

FIG. 2 is an external view of a cam shaft in the above embodiment.

FIG. 3 is a front view of each rotary disk in the embodiment.

FIG. 4 is a front view of an inner rotor and an outer rotor in the above embodiment.

FIG. 5 is an illustration corresponding to FIG. 1 of the second embodiment of the present invention.

FIG. 6 is an external view of a cam shaft and a rotary shaft according to a second embodiment of the present invention.

[Explanation of symbols]

 1a 1st inner rotor 1b 2nd inner rotor 2a 1st outer rotor 2b 2nd outer rotor 3 cam shaft 31 1st cam 32 2nd cam 4 coupling ring 5 housing 6,65 rotary discharge hole plate 61 discharge hole 7,75 rotation suction hole plate 71 Suction hole 9 Discharge port 10 Suction port 11 Rotating communication hole plate 12 Coupling member 13 Second rotating shaft

Claims (4)

[Claims] 1. An inner rotor having outer teeth having a trochoidal tooth profile, which is inserted into a camshaft so as to be able to revolve and rotate, is meshed with an outer rotor having inner teeth having a trochoidal tooth profile, and the meshing volume of the relative rotation of both rotors is increased. In a trochoidal fluid machine configured to deliver fluid from an intake port to a discharge port according to a change, a first cam and a second cam are provided at a phase of 180 ° in a circumferential direction on the cam shaft. A second inner rotor and a second inner rotor in the axial direction.
The first inner rotor is fitted to the first cam, the second inner rotor is fitted to the second cam so as to revolve and rotate, respectively, and the outer rotor and the first outer rotor are axially separated from each other. 2 outer rotors, the first inner rotor and the second inner rotor are fitted in this order to the inner teeth of both outer rotors, and a working fluid suction hole is provided and a rotary suction hole plate having an unbalanced weight A rotary discharge hole plate having a fluid discharge hole and having an unbalanced weight is attached to the cam shaft such that both unbalanced weights have a phase of 180 ° with each other and are rotatable in synchronization with the cam shaft. A fluid having a trochoidal tooth profile, which is configured to balance the unbalanced forces of the first and second inner rotor parts, and the rotary suction hole plate and the rotary discharge hole plate.械. 2. An inner rotor having outer teeth having a trochoidal tooth profile, which is inserted into a camshaft so as to be able to revolve and rotate, is meshed with an outer rotor having inner teeth having a trochoidal tooth profile, and the meshing volume of the relative rotation of both rotors is increased. In a trochoidal fluid machine configured to deliver fluid from an intake port to a discharge port according to a change, a first cam and a second cam are provided at a phase of 180 ° in a circumferential direction on the cam shaft. A second inner rotor and a second inner rotor in the axial direction.
The first inner rotor is fitted to the first cam, the second inner rotor is fitted to the second cam so as to revolve and rotate, respectively, and the outer rotor and the first outer rotor are axially separated from each other. 2 outer rotors, the first inner rotor and the second inner rotor are fitted in this order to the inner teeth of both outer rotors, and a working fluid suction hole is provided and a rotary suction hole plate having an unbalanced weight A rotary discharge hole plate having a fluid discharge hole and having an unbalanced weight is attached to the cam shaft such that both unbalanced weights have a phase of 180 ° with each other and are rotatable in synchronization with the cam shaft. The first and second inner rotor portions are configured to balance the unbalanced forces of the rotary suction hole plate and the rotary discharge hole plate, and the first inner rotor and the second inner rotor are And a camshaft that is fitted to the camshaft so as to be rotatable in synchronism with the camshaft and that communicates with the meshing volume of the first inner rotor and the first outer rotor and the meshing volume of the second inner rotor and the second outer rotor. A fluid machine equipped with a trochoidal tooth profile, characterized by having a communicating hole plate. 3. A fluid machine with a trochoidal tooth profile according to claim 1, wherein the first outer rotor and the second outer rotor are fixed to a housing together with a coupling ring interposed between the rotors. 4. The first outer rotor, the second outer rotor, and the coupling ring are connected to a second rotary shaft provided on the axially opposite side of the cam shaft, and are rotatable together with the second rotary shaft. A fluid machine provided with the trochoidal tooth profile according to items 1 and 2.