JP2518459B2 - Multi-cylinder rotary compressor - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a multi-cylinder rotary compressor used for refrigeration and air conditioning, and particularly to improvement of a vane of a compression mechanism section.

[Prior Art] A rotary compressor is used as a high-pressure compressor together with a reciprocating compressor, and is a mainstream of refrigerant and cooling compressors. As a conventional multi-cylinder rotary compressor of this type,
The techniques disclosed in Japanese Patent Laid-Open No. 63-113789 can be mentioned.

FIG. 8 is a longitudinal sectional view showing a conventional multi-cylinder rotary compressor,
FIG. 9 is a longitudinal sectional view of an essential part showing the main dimensions of an upper cylinder and a lower cylinder of a conventional multi-cylinder rotary compressor, FIG. 10 is a lateral sectional view of an essential part of FIG. 8, and FIG. FIG. 12 is a perspective view of a main part of the cylinder rotary compressor, and FIG. 12 is a perspective view of the vane of FIG. 11.

In the figure, 1 is a closed container, 2 is an electric motor part, 3 is a compression mechanism part, and 4 is a crankshaft for transmitting the rotational domain power of the electric motor part 2 to the compression mechanism part 3.

Reference numeral 5 denotes an upper cylinder arranged above the compression mechanism section 3,
Reference numeral 6 denotes a lower cylinder disposed below the compression mechanism portion, and as shown in FIG. 9, an inner diameter D1 of the upper cylinder 5, an inner diameter D2 of the lower cylinder 6, a height dimension H1 of the upper cylinder 5, and a lower cylinder. The height dimensions H2 of 6 are the same, that is, D1 = D2 and H1 = H2.

7 is an eccentric portion formed on the crankshaft 4 inside the upper cylinder 5, 8 is an eccentric portion formed on the crankshaft 4 with a phase difference of 180 degrees with the eccentric portion 7 inside the lower cylinder 6, 9 is a rolling piston rotatably attached to the eccentric portion 7 in the upper cylinder 5, 10 is a rolling piston rotatably attached to the eccentric portion 8 in the lower cylinder 6, and 11 is a bottom portion of the closed container 1. Is the lubricating oil injected into.

12 is a gas-liquid separator of refrigerant, and the separated gas is a suction pipe 13
, And the suction pipe 14 into the upper cylinder 5 and the lower cylinder 6, respectively. Reference numeral 15 is a check valve attached to the lower part of the suction pipe 13, and 16 is a spring 17 at the upper opening of the check valve 15.
A check valve body that is elastically pressed through the lubricating oil on the bottom of the closed container 1 when the electric motor section 2 stops rotating.
To prevent backflow from the upper cylinder 5 into the gas-liquid separator 12.

In FIGS. 10 to 12, 23 is a discharge valve device provided on the wall of the upper cylinder 5, 41 is reciprocating motion inside the vane groove 24 provided on the wall of the upper cylinder 5 via a spring 25. The leading end of the vane is in contact with the outer periphery of the rolling piston 9 so that the inside of the upper cylinder 5 is sucked into the suction chamber 27 and the compression chamber 28.
And separated. Reference numerals 26 and 42 denote springs and vanes provided on the wall of the lower cylinder 6.

Next, the operation of the conventional multi-cylinder rotary compressor configured as described above will be described.

When the electric motor section 2 is energized, the crankshaft 4 also rotates in conjunction with this. At the same time, the rolling piston 9 and the rolling piston 10 eccentrically rotate in the upper cylinder 5 and the lower cylinder 6, respectively, and along with this, the refrigerant sucked into the upper cylinder 5 and the lower cylinder 6 from the suction pipe 13 and the suction pipe 14, respectively. The gas is pressed by rolling piston 9 and rolling piston 10, respectively. At this time, the tips of the vanes 41 and 42 are always in contact with the outer peripheral surfaces of the rolling piston 9 and the rolling piston 10 by the elastic force of the springs 25 and 26.
The refrigerant gas in the lower cylinder 6 is blocked by the vanes 41 and 42, becomes high-temperature and high-pressure refrigerant gas, and is discharged into the closed container 1. Then, it is discharged to the outside of the closed container 1 through a discharge pipe (not shown).

Next, the vane 41 and the vane 42 are attached to the rolling piston 9
The force pressing the rolling piston 10 will be described.

The force for pressing the vane 41 against the rolling piston 9 is generated by the elastic force of the spring 25 and the difference between the pressure of the discharge gas discharged into the closed container 1 and the pressure of the gas inside the upper cylinder 5. Similarly, the force that presses the vane 42 against the rolling piston 10 is also generated by the elastic force of the spring 26 and the difference between the pressure of the discharge gas discharged into the closed container 1 and the pressure of the gas inside the lower cylinder 6. In order to balance the eccentric weight, the multi-cylinder rotary compressor uses the crankshaft 4 of each cylinder.
The eccentric part is arranged so as to change the phase with respect to the rotation direction. In this conventional example, as shown in FIG. 11, the eccentric portion 7 and the eccentric portion 8 of the crankshaft 4 are 180 degrees out of phase with each other. Therefore, when the rotation is stopped, the position of the rolling piston in each cylinder is different and the pressing force of the vane is different.

Here, taking the two-cylinder rotary compressor of this conventional example as an example, each action force involved in the reverse rotation when the multi-cylinder rotary compressor stops rotating will be described with reference to FIGS. 13 to 15. To do.

FIG. 13 is a model diagram showing the force acting on the compression mechanism portion of the multi-cylinder rotary compressor, FIG. 14 is a model diagram illustrating the force acting on the multi-cylinder rotary compressor and the reverse rotation phenomenon, and FIG. The figure is a model diagram showing the force acting in the single-cylinder rotary compressor.

In the figure, O is the center of rotation of the crankshaft 4, and coincides with the center of the inner diameter of the upper cylinder 5 and the lower cylinder 6. Z1 and Z2 are the centers of the eccentric part 7 of the upper cylinder 5 and the eccentric part 8 of the lower cylinder 6, respectively, and also coincide with the centers of the rolling piston 9 and the rolling piston 10. e is an eccentric length from the rotation center O of the crankshaft 4 to the center Z1 of the eccentric portion 7 and the center Z2 of the eccentric portion 8, and is equal in both the upper cylinder 5 and the lower cylinder 6, and a balance around the crankshaft 4 is maintained. There is.

F1 is the combined force of the spring 25 acting on the vane 41 and the pressure difference between the gas inside and outside the upper cylinder 5, and F2 is the same vane.
The combined force of the spring 26 acting on 42 and the pressure difference between the gas inside and outside the lower cylinder 6 causes the crankshaft 4 to move.
Acting toward the center of rotation O of. The contact point between the vane 41 and the rolling piston 9 and the contact point between the vane 42 and the rolling piston 10 are both on a curved surface, and F1 is Z1.
Direction component force Fv1 and tangential component force Fvr1. F2 is Z
It is divided into a component force Fv2 in two directions and a component force Fvr2 in a tangential direction. Further, with respect to the rotation center O of the crankshaft 4, X-Y
Considering the coordinates and expressing it as a component force in the X and Y directions, Fv
1 becomes Fvx1, Fvy1 and F2 becomes Fvx2, Fvy2.

When stopped at the position shown in Fig. 11, the Y-axis and line segment
The opening angle with OZ1 and the opening angle with the Y-axis and the line segment OZ2 are both D. And spring 25 is a spring
Compressed more than 26, and if the difference between the discharge pressure in the closed container 1 and the pressure in each cylinder is constant as ΔP, the force due to the pressure difference Fp
Is represented by Fp = ΔP · A · B (see FIG. 12), and the force Fp due to the differential pressure between the upper cylinder 5 and the lower cylinder 6 becomes equal, so the compression amount with respect to the natural length of the spring 25 and the spring 26. The difference between causes a difference between F1 and F2.

Therefore, in FIG. 13, F1> F2 and Fvy1
> Fvy2, the rolling piston 9 of the upper cylinder 5 is pushed down counterclockwise with respect to the rotation center O of the crankshaft 4, and the rolling piston 10 of the lower cylinder 6 is pushed up in the opposite direction. That is, the crankshaft 4 starts rotating in the opposite direction after stopping. At this time, the inertial rotational force m.
a (m is an eccentric weight, a is an acceleration around the crankshaft 4) is generated. When the state shown in FIG. 13 to FIG. 14 is reached, that is, when the crankshaft 4 rotates 90 degrees counterclockwise, the elastic forces of the spring 25 and the spring 26 become equal, and Fvy1−Fvy2 = 0 and Fvy1・ F-Fvy2 ・ f = 0 However, f is the length up to the point of action where the Y axis and vane press the rolling piston, and statically the forces around the rotation center O of the upper cylinder 5 and the lower cylinder 6 are balanced. However, the inertial rotational force m · a acts on Z1 and Z2 to generate a moment m · a · e around the rotation center O, and the upper cylinder 5 and the lower cylinder 6 act in the same counterclockwise direction. 2m ・ a ・ e
The inertia moment of acts to continue reverse rotation. This reverse rotation force is gradually reduced by the frictional force of the sliding portion, and when it becomes smaller than the frictional force, the reverse rotation is stopped.

By the way, in the case of a single-cylinder rotary compressor, as shown in FIG. 15, the pressing force of the vane given the inertial rotational force ma
Component force acting in the direction of the center Z3 of the rolling piston of F3
Fv3 acts in the direction of blocking the rotational inertial force from the Y axis,
The component force Fvy3 of v3 in the Y direction is Fvy3> m · a, and no reverse rotation occurs.

In this way, when the multi-cylinder rotary compressor is stopped and then reversely rotated, the lubricating oil 11 at the bottom of the hermetic container 1 flows from the sliding parts of the compression mechanism part 3 into the upper cylinder 5 and the lower cylinder 6. Since it enters and flows back through the suction pipe 13 and the suction pipe 14 into the gas-liquid separator 12 on the low pressure side, the lubricating oil 11 of the compression mechanism portion 3
Decrease. Therefore, at the time of restart, the lubricating oil becomes insufficient and the sliding portion is apt to seize. In order to prevent the lubricant oil 11 from being taken away by the reverse rotation immediately after the stop, a check valve 15 is provided in the suction pipe 13 to prevent the reverse rotation from starting and the lubricant oil 11 flowing into the suction pipe 13. are doing. As a result, the inside of the upper cylinder 5 provided with the check valve 15 is filled with the lubricating oil 11, the liquid compression state against the reverse rotation is generated, and the reverse rotation is stopped in a short time. Along with this, the lubricating oil 11 is also prevented from flowing backward from the lower cylinder 6 through the suction pipe 14 to the gas-liquid separator 12.

[Problems to be Solved by the Invention] Since the conventional multi-cylinder rotary compressor is configured as described above, it is necessary to attach the check valve 15 to either the suction pipe 13 or the suction pipe 14. In addition, a check valve 15 of high strength capable of withstanding the high pressure due to the liquid compression phenomenon during reverse rotation was required. Further, since the check valve 15 is attached, the cost is increased and high precision is required in manufacturing.

As another prior art, there is a technology disclosed in Japanese Utility Model Laid-Open No. 62-135885. However, in this type of technology, an upward force is always applied to the vertically slidable engagement pin, and when the crankshaft starts reverse rotation, the engagement pin projects and a recess provided on one thrust surface. This function prevents the crankshaft from rotating in reverse by performing the function of a meshing stopper. However, in this type of technology, the engagement pin is always in sliding contact with the thrust surface of the crankshaft at a predetermined pressure, the engagement pin and the thrust surface are cut from each other, and the shavings interfere with the movement of the engagement pin. However, there is a possibility that the engagement pin may break due to the contact resistance between the engagement pin and the thrust surface. Further, the engaging pin is always in sliding contact with the thrust surface of the crankshaft at a predetermined pressure, which increases the load on the electric motor side and wastes energy.

Therefore, the present invention, without attaching a check valve, and without additionally providing means for mechanically preventing reverse rotation,
A multi-cylinder rotary compressor that can prevent reverse rotation after rotation is stopped, prevent the lubricating oil in the closed container from flowing back into the gas-liquid separator on the low pressure side, and can prevent seizure of sliding parts. Is the challenge.

[Means for Solving the Problems] A multi-cylinder rotary compressor according to claim 1 transmits a rotational driving force of a plurality of cylinders arranged in a compression mechanism section and an electric motor section to the compression mechanism section, A crankshaft having eccentric parts having different phases in each cylinder, a rolling piston rotatably attached to an outer peripheral part of each eccentric part of the crankshaft, and an outer periphery of each rolling piston in contact with each other. Is divided into an intake chamber and a compression chamber for reciprocating movement, and each of the cylinders is provided with a vane having a different pressure receiving area.

A multi-cylinder rotary compressor according to claim 2, wherein rotational driving forces of a plurality of cylinders arranged in a compression mechanism section and an electric motor section are transmitted to the compression mechanism section, and eccentricity different in phase in each cylinder. A crankshaft having a portion, a rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and an outer periphery of each rolling piston, and partitioning each cylinder into an intake chamber and a compression chamber. And a reciprocating vane. The width dimension separating the intake chamber and the compression chamber of the vane is different for each cylinder, and the inner diameter and the height dimension of each cylinder are the same.

A multi-cylinder rotary compressor according to claim 3, wherein rotational driving forces of a plurality of cylinders arranged in a compression mechanism section and an electric motor section are transmitted to the compression mechanism section, and eccentricity having different phases in each cylinder. A crankshaft having a portion, a rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and an outer periphery of each rolling piston, and partitioning each cylinder into an intake chamber and a compression chamber. The vanes provided in each cylinder have different masses.

A multi-cylinder rotary compressor according to claim 4, wherein rotational driving forces of a plurality of cylinders arranged in a compression mechanism section and an electric motor section are transmitted to the compression mechanism section, and eccentricity having different phases in each cylinder. A crankshaft having a portion, a rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and an outer periphery of each rolling piston, and partitioning each cylinder into an intake chamber and a compression chamber. The vanes provided in each cylinder have different masses, and the mass difference is within 30%.

[Operation] In claim 1, since the vanes that are in contact with the outer periphery of each rolling piston and reciprocate by dividing the inside of each cylinder into the suction chamber and the compression chamber have different pressure receiving areas for each cylinder, The pressing force of the vanes caused by the differential pressure of the refrigerant gas inside and outside is different for each cylinder because the pressure receiving area of each vane is different. Now, when the crankshaft stops rotating, the vane pressing force varies due to the difference in the amount of expansion and contraction of the spring that elastically presses the vane against the rolling piston, and the vane tries to rotate in the reverse direction. On the other hand, the difference in the pressing force of the vane caused by the differential pressure of the refrigerant gas inside and outside the cylinder acts in the direction of preventing the reverse rotation.

In the second aspect, since the width of each vane is different for each cylinder, the pressing force of the vane caused by the differential pressure of the refrigerant gas inside and outside the cylinder is different for each cylinder due to the different pressure receiving area of each vane. different. Now, when the crankshaft stops rotating, the pressing force of the vane differs due to the difference in the amount of expansion and contraction of the spring that elastically presses the vane against the rolling piston, and therefore tries to rotate in the reverse direction. On the other hand, the difference in the pressing force of the vane caused by the differential pressure of the refrigerant gas inside and outside the cylinder acts in the direction of preventing the reverse rotation.

In the third aspect, since the vanes of the cylinders have different masses for each cylinder, the pressing force of the vanes caused by the differential pressure of the refrigerant gas inside and outside the cylinder is different for each cylinder. Therefore, similarly to the first aspect, the difference in the pressing force of the vanes caused by the differential pressure of the refrigerant gas inside and outside the cylinder acts in the direction of preventing the reverse rotation when the rotation of the crankshaft is stopped.

According to the fourth aspect, since the vanes of each cylinder have different masses for each cylinder, the pressing force of the vanes caused by the differential pressure of the refrigerant gas inside and outside the cylinder differs for each cylinder. Moreover, by changing the vanes to materials with different masses so that the mass difference between the vanes is within 30%,
Vibration can be maintained at the conventional level. Therefore, similarly to the first aspect, the difference in the pressing force of the vanes caused by the differential pressure of the refrigerant gas inside and outside the cylinder acts in the direction of preventing the reverse rotation when the rotation of the crankshaft is stopped.

[Embodiment] <First Embodiment> A first embodiment of the present invention will be described below with reference to FIGS. 1 to 3.

1 is a perspective view of a main part of a multi-cylinder rotary compressor according to a first embodiment of the present invention, FIG. 2 is a perspective view of an upper vane of FIG. 1, and FIG. 3 is a lower vane of FIG. FIG. In the figure, the same reference numerals as those in FIGS. 8 to 12 are the same as or correspond to the conventional constituent parts, and therefore the description thereof will be omitted here.

In the figure, reference numeral 21 denotes a vane that reciprocates inside a vane groove 24 provided in a wall portion of the upper cylinder 5 via a spring 25. The inside of is separated into a suction chamber 27 and a compression chamber 28. Reference numeral 22 denotes a vane that reciprocates inside a vane groove (not shown) provided in the wall portion of the lower cylinder 6 via a spring 26. The dimensions of the vanes 21 are formed as shown in FIG. 2, and the dimensions of the vanes 22 are formed as shown in FIG. 3, and the vanes 21 and 22 have width dimensions A1 and A2. Only different. That is, A1 <A2
Is.

Next, the acting force applied to the vanes 21 and 22 of the multi-cylinder rotary compressor of the first embodiment configured as described above will be described.

The force F1 acting on the vane 21 is a combination of the force due to the differential pressure of the refrigerant gas inside and outside the upper cylinder 5 and the elastic force of the spring 25. Further, the force F2 acting on the vane 22 is the lower cylinder 6
The force due to the differential pressure between the refrigerant gas inside and outside and the elastic force of the spring 26 are combined. Now, if the force due to the pressure difference ΔP between the refrigerant gas inside and outside the upper cylinder 5 is Fp1, then Fp1 = ΔP · A1 · B, while if the force due to the pressure difference ΔP between the refrigerant gas inside and outside the lower cylinder 6 is Fp2, then Fp2 = ΔP · A2 · B. If the difference between the forces Fp1 and Fp2 is ΔFp, then ΔFp = Fp2-Fp1 = ΔP · (A2-A1) · B> 0. Therefore, immediately after the operation is stopped, when reverse rotation is started and the state shown in FIG. 14 is reached, ΔFp · f is applied to the reverse rotation inertia moment 2m · a · e acting about the rotation center O.
A reverse rotation blocking moment is generated. Therefore, the width dimension A1 of the vane 21 and the width dimension A2 of the vane 22 are set so that ΔFp · f> 2m · a · e.
If is set, reverse rotation does not occur.

By the way, the multi-cylinder rotary compressor has a characteristic that the eccentric part mass is arranged in equilibrium with respect to the rotation center of the crankshaft 4 as compared with the single-cylinder rotary compressor, and thus has a characteristic of less vibration during operation. Therefore, the mass of the vanes 21 and 22 also contributes to the mass of the eccentric portion.

That is, the upper cylinder 5 and the lower cylinder 6 are arranged in the compression mechanism section 3, and the rotational driving force of the electric motor section 2 is transmitted to the compression mechanism section 3 so that the eccentric section 7 and the eccentric section having different phases in each cylinder. A crankshaft 4 having a rolling shaft 8, a rolling piston 9 and a rolling piston 10 rotatably attached to the outer periphery of the eccentric portion 7 and the eccentric portion 8 of the crankshaft 4, and the outer periphery of the rolling piston 9 and the rolling piston 10. A vane 21 and a vane 22 that reciprocate by abutting against the suction chamber 27 and the compression chamber 28 are provided,
The vanes 21 and 22 provided in the upper cylinder 5 and the lower cylinder 6 have different masses. Therefore, since the mass of each vane 21 and the vane 22 is different for each cylinder, the vane 21 caused by the differential pressure of the refrigerant gas inside and outside the cylinder is generated.
The pressing force of the vanes 22 differs from cylinder to cylinder due to the different pressure receiving areas of the vanes 21 and 22. Therefore,
The pressure difference between the vanes 21 and 22 caused by the pressure difference between the refrigerant gas inside and outside the upper cylinder 5 and the lower cylinder 6 prevents reverse rotation when the rotation of the crankshaft 4 is stopped. It is possible to prevent the lubricating oil from flowing back to the gas-liquid separator 12 and prevent the seizure of the sliding portion.

Further, when the width dimension of the vanes 21 and 22 is changed for each cylinder, vibration during operation increases. Therefore, in this case, by changing the vanes 21 and 22 to materials having different specific gravities so that the mass difference between the vanes is within 30%, the vibration can be maintained at the conventional level.

That is, the upper cylinder 5 and the lower cylinder 6 are arranged in the compression mechanism section 3, and the rotational driving force of the electric motor section 2 is transmitted to the compression mechanism section 3 so that the eccentric section 7 and the eccentric section having different phases in each cylinder. A crankshaft 4 having a rolling shaft 8, a rolling piston 9 and a rolling piston 10 rotatably attached to the outer periphery of the eccentric portion 7 and the eccentric portion 8 of the crankshaft 4, and the outer periphery of the rolling piston 9 and the rolling piston 10. A vane 21 and a vane 22 that reciprocate by abutting against the suction chamber 27 and the compression chamber 28 are provided,
The vanes 21 and 22 provided in the upper cylinder 5 and the lower cylinder 6 have different masses, and the mass difference is within 30%. Therefore, since the mass of each vane 21 and the vane 22 is different between the upper cylinder 5 and the lower cylinder 6, the pressing force of the vane 21 and the vane 22 caused by the differential pressure of the refrigerant gas inside and outside the upper cylinder 5 and the lower cylinder 6 is It works in a direction to prevent reverse rotation when the rotation of the shaft 4 stops. Also, each vane 21 and vane 22
Due to the different pressure receiving area of each cylinder,
By changing the vanes 21 and 22 to materials having different masses so that the mass difference between the vanes 21 and 22 is within 30%, the vibration can be maintained at the conventional level. As a result, the reverse rotation after the rotation is stopped is prevented, so that the lubricating oil in the closed container 1 can be prevented from flowing back to the gas-liquid separator 12, and the sliding portion can be prevented from being seized.

Also, when the mass of the vane changes, it is necessary to change the elastic force of the spring that is involved in the reciprocating motion of the vane. Generally, by changing the spring constant, the structure that does not interfere with the reciprocating motion of the vane should be obtained. You can

As described above, in the multi-cylinder rotary compressor of the above-described embodiment, the upper cylinder 5 and the lower cylinder 6 are arranged in the compression mechanism section 3, and the rotational driving force of the electric motor section 2 is transmitted to the compression mechanism section 3. A crankshaft 4 having an eccentric portion 7 and an eccentric portion 8 having different phases in each cylinder, and the crankshaft 4
Rolling piston 9 and rolling piston 10 rotatably mounted on the outer periphery of the eccentric portion 7 and the eccentric portion 8
And the rolling piston 9 and the rolling piston
A vane 21 and a vane 22 that reciprocate by partitioning the suction chamber 27 and the compression chamber 28 into contact with the outer peripheral portion of 10 are provided, and the width dimension separating the suction chamber 27 and the compression chamber 28 of these vanes 21 and 22 is Differently, the inner diameter D1 of the upper cylinder 5 and the inner diameter D2 of the lower cylinder 6 and the height dimension H1 of the upper cylinder 5 and the height dimension H2 of the lower cylinder 6 are the same.

Therefore, according to the above-described embodiment, since the width dimension of each vane 21, 22 is made different for each cylinder, the pressing force of the vane generated by the differential pressure of the refrigerant gas inside and outside the cylinder is equal to that of each vane 21, 22. Since the pressure receiving area is different, it is different for each cylinder. This difference in pressing force acts in a direction to prevent the reverse rotation due to the difference in expansion / contraction amount of the spring 25 and the spring 26 immediately after the crankshaft 4 stops rotating, thereby preventing reverse rotation. As a result, the lubricating oil 11 in the closed container 1 can be prevented from flowing back to the gas-liquid separator 12 and taken out, and the seizure of the sliding portion can be prevented.

By the way, the vane 21 and the vane 22 of the above embodiment, the width dimension A2 of the vane 22 is made larger than the width dimension A1 of the vane 21, but in the case of carrying out the present invention, it is not limited to this. Not, conversely, the width dimension A1 of vane 21 to vane 22
Even if the width is larger than the width A2, the same effect can be obtained.

<Second Embodiment> Next, a second embodiment of the present invention will be described with reference to FIGS. 4 to 7.

FIG. 4 is a longitudinal sectional view of a main part showing main dimensions of an upper cylinder and a lower cylinder in a multi-cylinder rotary compressor according to a second embodiment of the present invention, and FIG. 5 is a multi-cylinder rotation according to a second embodiment of the present invention. 6 is a perspective view of an upper vane of FIG. 5, and FIG. 7 is a perspective view of a lower vane of FIG. 5.

In the figure, reference numeral 31 is a crankshaft for transmitting the rotary section power of the electric motor section 2 to the compression mechanism section 3.

Reference numeral 32 denotes an upper cylinder arranged above the compression mechanism section 3, and 33 denotes a lower cylinder arranged below the compression mechanism section 3, as shown in FIG. 33 inner diameter D4
The dimensional relationship of is D3> D4. Further, the dimensional relationship between the height dimension H3 of the upper cylinder 32 and the height dimension H4 of the lower cylinder 33 is H3 <H4
Is.

34 is a crankshaft inside the upper cylinder 32
An eccentric portion formed on the crankshaft 31 has a phase difference of 180 degrees with the eccentric portion 34 inside the lower cylinder 33, and an eccentric portion 35 is formed on the upper cylinder.
A rolling piston rotatably attached to the eccentric portion 34 in 32, 37 a rolling piston rotatably attached to the eccentric portion 35 in the lower cylinder 33, and 38 a vane provided on the wall of the upper cylinder 32. Reference numeral 39 denotes a vane that reciprocates inside the groove via a spring 25, and 39 denotes a vane that reciprocates inside the groove of the vane provided in the wall of the lower cylinder 33 via the spring 26.

Each dimension of the vane 38 is formed as shown in FIG.
Since the height dimension B1 corresponds to the height dimension H3 of the upper cylinder 32,
B1 = H3. Further, each dimension of the vane 39 is formed as shown in FIG. 7, and the height dimension B2 is the height dimension of the lower cylinder 33.
Since it corresponds to H4, there is a relation of B2 = H4. That is, since H3 <H4 as described above, B1 <B2.

Here, the excluded volume of each cylinder (stroke volume)
Will be described.

As shown in FIG. 5, set the outer diameter of the rolling piston 36 to
D5, when the outer diameter of the rolling piston 37 and D6, the displacement volume Vu of the upper cylinder 32, Vu = π · (D3 2 -D5 2) · H3 / 4, displacement volume V1 of the lower cylinder 33, V1 = [pi・ (D4 ² −D6 ² ) · H4 / 4 {where π: pi}. These upper cylinders
If the ratio (Vu-V1) / Vu or (Vu-V1) / V1 of the excluded volume between 32 and lower cylinder 33 exceeds 20%, the required power difference between upper cylinder 32 and lower cylinder 33 during the compression process Crankshaft 31 resulting from
The fluctuation of the rotation speed is increased, and the vibration of the compressor is increased.
Therefore, the above major dimensions: D3, D4, D5, D6, H3, H4
In the above setting, the main dimensions are adjusted so that the ratio of the excluded volumes of the upper cylinder 32 and the lower cylinder 33 is within 20%.

Next, the acting force applied to the vanes 38 and 39 of the multi-cylinder rotary compressor of the second embodiment configured as described above will be described.

The force F1 acting on the vane 38 is a combination of the force due to the differential pressure of the refrigerant gas inside and outside the upper cylinder 32 and the elastic force of the spring 25. Also, the force F2 acting on the vane 39 is the lower cylinder 33
The force due to the differential pressure between the refrigerant gas inside and outside and the elastic force of the spring 26 are combined. Now, if the force due to the pressure difference ΔP of the refrigerant gas inside and outside the upper cylinder 32 is Fp1, then Fp1 = ΔP · A · B1, and if the force due to the pressure difference ΔP between the refrigerant gas inside and outside the lower cylinder 33 is Fp2, then Fp2 = ΔP · A · B2. When the difference between the forces Fp1 and Fp2 is ΔFp, ΔFp = Fp2-Fp1 = ΔP · A · (B2-B1)> 0. Therefore, immediately after the operation is stopped, when reverse rotation is started and the state shown in FIG. 14 is reached, ΔFp · f is applied to the reverse rotation inertia moment 2m · a · e acting about the rotation center O.
A reverse rotation blocking moment is generated. Therefore, if the height dimension B1 of the vane 38 and the height dimension B2 of the vane 39 are set so that ΔFp · f> 2m · a · e, reverse rotation does not occur.

As described above, in the multi-cylinder rotary compressor of this embodiment, the upper cylinder 32 and the lower cylinder 33 are arranged in the compression mechanism section 3, and the rotational driving force of the electric motor section 2 is transmitted to the compression mechanism section 3. A crankshaft 31 having an eccentric portion 34 and an eccentric portion 35 having different phases in each cylinder, and the crankshaft 31.
The rolling piston 36 and the rolling piston 37 rotatably mounted on the outer peripheral portions of the eccentric portion 34 and the eccentric portion 35 of
And the rolling piston 36 and the rolling piston
A vane 38 and a vane 39 that reciprocate by partitioning the suction chamber 27 and the compression chamber 28 into contact with the outer peripheral portion of the 37 are provided, and a height dimension that partitions the suction chamber 27 and the compression chamber 28 of the vane 38 and the vane 39. Are different, the inner diameter D3 of the upper cylinder 32 and the lower cylinder 33
The inner diameter D4, the height dimension H3 of the upper cylinder 32, and the height dimension H4 of the lower cylinder 33 are different from each other.

Therefore, according to this embodiment, the inner diameter and height of each cylinder are made different for each cylinder, and the height of each vane is made different for each cylinder. The pressing force of the vanes generated by the above is different for each cylinder because the pressure receiving area of each vane is different. The difference in the pressing force is the same as in the first embodiment.
Immediately after the 31 stops rotating, the spring 25 and the spring
Due to the difference in the amount of expansion and contraction of 26, it works in the direction that prevents it from trying to rotate in the reverse direction, and prevents reverse rotation. by this,
It is possible to prevent the lubricating oil 11 in the closed container 1 from flowing back to the gas-liquid separator 12 and carried out, and to prevent seizure of the sliding portion.

By the way, the vane 38 and the vane 39 of this second embodiment
The height dimension B2 of the vane 39 is made larger than the height dimension B1 of the vane 38.However, the present invention is not limited to this, and the upper cylinder 32 and the lower cylinder 33 are not limited thereto.
By changing the main dimension of the vane 38, the height B1 of the vane 38 can be made larger than the height B2 of the vane 39, and the same effect can be obtained.

Further, the vanes 38 and 39 of the second embodiment are different only in the height dimension, but may be different in the width dimension. However, as a matter of course, when changing both the height dimension and the width dimension, it is necessary to prevent the pressure receiving areas of the vanes from being equal.

That is, in each of the above-described embodiments, the upper cylinder 5 and the lower cylinder 6 are arranged in the compression mechanism section 3, and the rotational driving force of the electric motor section 2 is transmitted to the compression mechanism section 3 so that the phases are different in each cylinder. Crankshaft 4 having eccentric portion 7 and eccentric portion 8
And a rolling piston 9 rotatably attached to the outer peripheral portions of the eccentric portion 7 and the eccentric portion 8 of the crankshaft 4.
And the rolling piston 10 and the suction chamber by contacting the rolling piston 9 and the outer peripheral portion of the rolling piston 10.
A vane 21 and a vane 22 which reciprocate by partitioning the vane 21 and the compression chamber 28 are provided, and a suction chamber for the vane 21 and the vane 22.
The pressure receiving area that separates the compression chamber 28 and the compression chamber 28 is different for each of the upper cylinder 5 and the lower cylinder 6. Therefore,
Since the pressure receiving area of each vane 21 and vane 22 is different for each of the upper cylinder 5 and the lower cylinder 6, the vane 21 and the vane caused by the differential pressure of the refrigerant gas inside and outside the upper cylinder 5 and the lower cylinder 6 are generated.
The pressing force of 22 differs for each of the upper cylinder 5 and the lower cylinder 6 due to the different pressure receiving areas of the vanes 21 and 22. This difference in pressing force prevents the crankshaft 4 from trying to rotate in the reverse direction immediately after the rotation is stopped, so that the lubricating oil in the closed container 1 can be prevented from flowing back into the gas-liquid separator 12. It is possible to prevent seizure of the sliding portion.

Although each of the above-described embodiments shows the case where the invention is applied to a two-cylinder rotary compressor, the present invention is not limited to this, and even if the number of cylinders further increases,
The same effect can be obtained.

EFFECTS OF THE INVENTION As described above, the multi-cylinder rotary compressor according to claim 1 has a plurality of cylinders arranged in the compression mechanism section, and transmits the rotational driving force of the electric motor section to the compression mechanism section. A crankshaft having eccentric parts with different phases in each cylinder, a rolling piston rotatably attached to the outer peripheral part of each eccentric part of the crankshaft, and an outer periphery of each rolling piston, in contact with each cylinder. While the reciprocating motion is divided into a suction chamber and a compression chamber, a vane having a different pressure receiving area is provided for each cylinder, and the pressure receiving area separating the suction chamber and the compression chamber of these vanes is made different for each cylinder. is there. Therefore, since the pressure receiving area of each vane is different for each cylinder, the pressing force of the vane caused by the differential pressure of the refrigerant gas inside and outside the cylinder is different for each cylinder due to the different pressure receiving area of each vane. This difference in pressing force prevents the crankshaft from trying to reversely rotate immediately after the rotation of the crankshaft is stopped, so that the lubricating oil in the closed container can be prevented from flowing backward to the gas-liquid separator. It is possible to prevent seizure of moving parts.

The multi-cylinder rotary compressor according to claim 2, wherein a plurality of cylinders are arranged in the compression mechanism section, and the rotational driving force of the electric motor section is transmitted to the compression mechanism section so that eccentric sections having different phases are formed in each cylinder. A crankshaft having the same, a rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and a reciprocating motion that contacts the outer periphery of each rolling piston to partition the inside of the cylinder into a compression chamber and a suction chamber The width dimension that separates the suction chamber and the compression chamber of these vanes is different for each cylinder, and the inner diameter and the height dimension of each cylinder are the same. Therefore, since the width dimension of each vane is different for each cylinder, the pressing force of the vane caused by the differential pressure of the refrigerant gas inside and outside the cylinder is different for each cylinder because the pressure receiving area of each vane is different. This difference in pressing force prevents the crankshaft from trying to reversely rotate immediately after the rotation of the crankshaft is stopped, so that the lubricating oil in the closed container can be prevented from flowing backward to the gas-liquid separator. It is possible to prevent seizure of moving parts.

A multi-cylinder rotary compressor according to claim 3, wherein a plurality of cylinders are provided in the compression mechanism section, and the rotational driving force of the electric motor section is transmitted to the compression mechanism section so that the eccentric sections having different phases in the respective cylinders. And a rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and a reciprocating partition of the inside of the cylinder into a compression chamber and a suction chamber in contact with the outer periphery of each rolling piston. The moving vane is provided, and the vane provided in each cylinder is
Each has a different mass. Therefore, since the mass of each vane is different for each cylinder, the pressing force of the vane caused by the differential pressure of the refrigerant gas inside and outside the cylinder is different for each cylinder due to the different pressure receiving area of each vane. Therefore, the difference in the pressing force of the vane caused by the differential pressure of the refrigerant gas inside and outside the cylinder prevents reverse rotation when the rotation of the crankshaft stops, so that the lubricating oil in the closed container flows backward to the gas-liquid separator. It is possible to prevent the sliding, and it is possible to prevent seizure of the sliding portion.

A multi-cylinder rotary compressor according to claim 4, wherein a plurality of cylinders are arranged in the compression mechanism section, and the rotational driving force of the electric motor section is transmitted to the compression mechanism section so that the eccentric sections having different phases in the respective cylinders. And a rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and a reciprocating partition of the inside of the cylinder into a compression chamber and a suction chamber in contact with the outer periphery of each rolling piston. The moving vane is provided, and the vane provided in each cylinder is
Make each mass different, and the difference in mass is
It is within 30%. Therefore, since the mass of each vane is different for each cylinder, the pressing force of the vane caused by the differential pressure of the refrigerant gas inside and outside the cylinder acts in the direction of preventing reverse rotation when the rotation of the crankshaft is stopped. Also, because the pressure receiving area of each vane is different, it varies from cylinder to cylinder, but by changing the vanes to materials with different masses so that the mass difference of each vane is within 30%,
Vibration can be maintained at the conventional level. by this,
Since the reverse rotation after the rotation is stopped is prevented, it is possible to prevent the lubricating oil in the closed container from flowing back to the gas-liquid separator.
It is possible to prevent seizure of the sliding portion.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a main part of a multi-cylinder rotary compressor according to a first embodiment of the present invention, FIG. 2 is a perspective view of an upper vane of FIG. 1, and FIG. FIG. 1 is a perspective view of a lower vane of FIG. 1, and FIG. 4 is a longitudinal sectional view of an essential part showing main dimensions of an upper cylinder and a lower cylinder in a multi-cylinder rotary compressor according to a second embodiment of the present invention.
FIG. 6 is a perspective view of a main part of a multi-cylinder rotary compressor according to a second embodiment of the present invention, FIG. 6 is a perspective view of an upper vane of FIG. 5, and FIG. 7 is a perspective view of a lower vane of FIG. FIG. 8 is a vertical cross-sectional view showing a conventional multi-cylinder rotary compressor, and FIG. 9 is a longitudinal cross-sectional view of a main part showing the main dimensions of an upper cylinder and a lower cylinder of a conventional multi-cylinder rotary compressor. FIG. 10 is a cross-sectional view of the main part of FIG.
FIG. 11 is a perspective view of a main part of a conventional multi-cylinder rotary compressor, FIG. 12 is a perspective view of a vane of FIG. 11, and FIG. 13 is a force acting on a compression mechanism part of the multi-cylinder rotary compressor. FIG. 14 is a model diagram for explaining the force acting in the multi-cylinder rotary compressor and the reverse rotation phenomenon, and FIG. 15 is a model diagram showing the force acting in the single-cylinder rotary compressor. In the figure, 2: electric motor part, 3: compression mechanism part 4,31: crankshaft 5,32: upper cylinder, 6,33: lower cylinder 7,8,34,35: eccentric part 9,10,36,37: Rolling pistons 21,22,38,39: vanes 27: suction chamber, 28: compression chamber. In the drawings, the same reference numerals and symbols indicate the same or corresponding parts.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Taiichi Kobayakawa 3-18-1 Oshika, Shizuoka-shi, Shizuoka Mitsubishi Electric Corporation Shizuoka Factory (72) Inventor Satoshi Suzuki 3-18-1 Oka, Shizuoka-shi No. Mitsubishi Electric Co., Ltd. Shizuoka Works (72) Inventor Yoshinori Shirato 3-18-1, Oga Shizuoka-shi, Shizuoka Prefecture Mitsubishi Electric Co., Ltd. Shizuoka Works (72) Shoji Hagiwara 3-18, Oka, Shizuoka-shi No. 1 Mitsubishi Electric Co., Ltd. Shizuoka Factory

Claims (4)

(57) [Claims] 1. A plurality of cylinders arranged in a compression mechanism section, a crankshaft having an eccentric section having a different phase in each cylinder for transmitting a rotational driving force of an electric motor section to the compression mechanism section, and A rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and an outer periphery of each rolling piston in contact with each other, and reciprocating by dividing the inside of each cylinder into an intake chamber and a compression chamber, and A multi-cylinder rotary compressor, comprising: vanes each having a different pressure receiving area. 2. A plurality of cylinders arranged in a compression mechanism section, a crankshaft having an eccentric section having a different phase in each cylinder for transmitting the rotational driving force of an electric motor section to the compression mechanism section, A rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and a vane that contacts the outer periphery of each rolling piston and reciprocates by partitioning the inside of each cylinder into an intake chamber and a compression chamber. A multi-cylinder rotary compressor is characterized in that the width dimension separating the vane suction chamber and the compression chamber is different for each cylinder, and the inner diameter and the height dimension of each cylinder are the same. 3. A plurality of cylinders arranged in a compression mechanism portion, a crankshaft having an eccentric portion having a different phase in each cylinder, which transmits rotational driving force of an electric motor portion to the compression mechanism portion, and A rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and a vane that contacts the outer periphery of each rolling piston and reciprocates by partitioning the inside of each cylinder into an intake chamber and a compression chamber. However, the vanes provided in each cylinder have different masses, so that the multi-cylinder rotary compressor is characterized. 4. A plurality of cylinders arranged in a compression mechanism section, a crankshaft having an eccentric portion having a different phase in each cylinder, which transmits rotational driving force of an electric motor section to the compression mechanism section, and A rolling piston rotatably attached to the outer peripheral portion of each eccentric portion of the crankshaft, and a vane that contacts the outer periphery of each rolling piston and reciprocates by partitioning the inside of each cylinder into an intake chamber and a compression chamber. However, the vanes provided in each cylinder have different masses,
The multi-cylinder rotary compressor is characterized in that the mass difference is within 30%.