JPH0666277A - Rotary compressor - Google Patents

Abstract

(57) [Summary] [Objective] The revolution speed of the roller 34 in the high-pressure rotation region is slowed down, the revolution speed in the low-pressure rotation region is increased, and the flow velocity of the high-pressure fluid discharged from the compression chamber 6 is reduced to prevent overcompression. Reduced,
It improves compression efficiency, reduces power fluctuations, and suppresses vibration and noise. [Structure] A crankshaft 4 is divided into a motor-side crankshaft 42 connected to a motor 2 and a cylinder-side crankshaft 43. An eccentric pin portion 41 that fits into the roller 34 is formed on the cylinder side crankshaft 43, and a rotation transmitting portion 44 that extends radially outward is formed at the end of the connecting side shaft of the motor side crankshaft 42 to the eccentric pin portion 41. Form. Eccentric pin portion 41,
The long groove 4 extending outward in the radial direction is provided on one side of the rotation transmitting portion 44.
5, and a pin 46 that slidably engages with the long groove 45 is provided on the other side. In addition, the motor side crankshaft 4
The axis O of 2 is set to the center S of the cylinder chamber 30 and the compression chamber 6
Is eccentric to the high-pressure rotation region side, which is smaller than the suction chamber 5.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor used as a refrigerant compressor or the like in a refrigeration system.

[0002]

2. Description of the Related Art Conventionally, this type of compressor has been disclosed in
As disclosed in Japanese Patent No. 114093 and as shown in FIG. 9, a single cylinder C having a circular cylinder chamber Q and an eccentric pin portion E of a crankshaft D are revolved inside the cylinder chamber Q. A roller R formed of a cylinder, and a blade B having a head contacting the outer peripheral surface of the roller R to partition the inside of the cylinder chamber Q into a suction chamber L and a compression chamber H, and a low pressure sucked from a suction port J. The gas is compressed and the high pressure gas is discharged from the discharge port K. Further, in the above configuration, the axis O of the crankshaft D is made to coincide with the center S of the cylinder chamber Q, and as shown by the dotted line in FIG. The revolution speed ωc of the roller R has a constant value in synchronization with the rotation of the crankshaft D over the entire rotation angle of.

[0003]

However, in the above, since the revolution speed of the roller R is constant over the entire rotation angle, the flow velocity of the high-pressure discharge gas discharged from the discharge port K is large, and therefore, Particularly, in a compressor for high speed rotation, there is a problem that over-compression occurs and power loss is caused and compression efficiency is reduced.

Further, as shown in FIG. 6, the compression load torque T with respect to the rotation angle of the crankshaft D shows a large change in the high pressure rotation region in the latter half of the rotation angle where the volume of the compression chamber H is narrowed. The compression power P1 obtained by the product of T and the revolution speed ωc of the roller R changes as shown by the dotted line in FIG. 7, and the average power Pa in the low-pressure rotation region in the first half of the rotation angle and the high-pressure rotation region in the second half of the rotation angle There is also a problem that the difference is large and vibration and noise due to power fluctuations increase.

The present invention has been made in view of the above problems, and an object thereof is to reduce the revolution speed of the roller in a high-pressure rotation region by adding a unique device to the revolution mechanism of the roller with respect to the cylinder chamber. In addition, it is possible to reduce the overcompression due to the low speed of the discharge fluid, reduce the fluctuation of the compression power with respect to the rotation angle, and reduce the vibration and noise.

[0006]

In order to achieve the above object, the present invention comprises a motor 2 and a compression element 3, the compression element 3 having a cylinder 31 having a cylinder chamber 30 and the motor 2. The roller 3 that fits into the eccentric pin portion 41 of the crankshaft 4 to be connected and revolves inside the cylinder chamber 30.
4, a suction chamber 5 and a compression chamber 6 inside the cylinder chamber 30.
In a rotary compressor provided with a blade 36 that divides into a cylinder, a motor-side crankshaft 42 that is connected to the motor 2 and a cylinder-side crankshaft 43 are formed separately, and the cylinder-side crankshaft 43 is provided inside the roller 34. An eccentric pin portion 41 to be fitted to the eccentric pin portion, and a rotation transmitting portion 44 extending radially outward is formed at an end portion of the motor-side crankshaft 42 connected to the eccentric pin portion 41. A long groove 45 extending outward in the radial direction is formed on one of the portion 41 and the rotation transmitting portion 44, and a pin 46 slidably engaged with the long groove 45 is provided on the other of the portion 41 and the rotation transmitting portion 44. The axis O of the crankshaft 42 is eccentric with respect to the center S of the cylinder chamber 30 toward the high pressure rotation region side where the compression chamber 6 is smaller than the suction chamber 5.

The outer peripheral cylindrical surface 34a of the roller 34
The blade 34 is provided in a protruding manner, and the protruding tip side of the blade 36 is engaged with the rocking body 7 that rotatably supports the outside of the cylinder chamber 30 so as to move back and forth, so that the roller 34 is configured to be non-rotating. Preferably.

[0008]

When the motor-side crankshaft 42 rotates due to the rotational driving of the motor 2, the eccentric pin portion formed on the cylinder-side crankshaft 43 with respect to the rotation angle of the motor-side crankshaft 42 in the low-pressure rotation region. Since the rotation angle of 41 increases, the roller 34 that revolves with the rotation of the eccentric pin portion 41 revolves faster than the rotation speed of the crankshaft 4, and in the high-pressure rotation region, the motor-side crankshaft Since the rotation angle of the eccentric pin portion 41 formed on the cylinder side crankshaft 43 becomes smaller than the rotation angle of 42, the roller 34 revolves slower than the rotation speed of the crankshaft 4.

Therefore, the revolution speed of the roller 34 in the high pressure rotation region becomes slower than the revolution speed in the low pressure rotation region. In this way, the flow velocity of the high-pressure fluid discharged from the compression chamber 6 can be reduced by the amount by which the rotation speed of the roller 34 in the high-pressure rotation region becomes slower, whereby overcompression can be reduced and reduction in compression efficiency can be suppressed.

Moreover, since the revolution speed of the roller 34 in the high pressure rotation region is low and the revolution speed in the low pressure rotation region is high, the compression power obtained by the product of the compression load torque and the revolution speed of the roller 34 is Compared with the conventional one whose revolution speed is constant, it can be reduced in the high-pressure rotation region, and
It can be increased in the low-pressure rotation region, and thus power fluctuation can be reduced, so that vibration and noise can be suppressed.

Further, in the above-mentioned case, the oscillating body 7 which projects the blade 36 on the outer peripheral cylindrical surface 34a of the roller 34 and rotatably supports the protruding tip side of the blade 36 to the outside of the cylinder chamber 30. When the roller 34 is made to be a non-rotating type by freely engaging with and retracting from the compression chamber 6 to the suction chamber 5 through the gap between the outer peripheral cylindrical surface 34a of the roller 34 and the blade 36. The fluid can be prevented from leaking, and the volumetric efficiency can be improved.

[0012]

1 shows a rotary compressor for compressing a refrigerant, in which a motor 2 is arranged in an upper inner part of a hermetic casing 1 and a cylinder 3 is arranged below the motor 2.
1 and a compression element 3 composed of a front head 32 and a rear head 33 arranged at the upper and lower positions of the cylinder 31, and a crankshaft 4 extending from the motor 2 is interlocked with the compression element 3.

The cylinder 31 of the compression element 3 forms a circular cylinder chamber 30, and a roller 34 is rotatably mounted in the cylinder chamber 30. Then, the eccentric pin portion 41 of the drive shaft 4 is fitted into the roller 34, and the roller 34 is moved to the cylinder chamber 3 as the drive shaft 4 is driven.
Eccentric rotation is performed within 0.

Further, as shown in FIGS. 2 to 4, a low pressure gas refrigerant is supplied to the cylinder 31 in the cylinder 31.
A suction hole 35 for sucking in the
The blade 36 is in contact with the tip of the blade and slides so as to move back and forth to partition the cylinder chamber 30 into the suction chamber 5 and the compression chamber 6.
And a discharge port 3 that discharges the compressed gas refrigerant
7 is provided, and the rotation of the roller 34 accompanying the rotational driving of the motor 2 causes the cylinder chamber 3
The low-pressure gas refrigerant is sucked into the inside of the casing 0, the sucked gas refrigerant is compressed by the rotation of the roller 34, and the compressed gas refrigerant is discharged from the discharge port 37 into the casing 1.

In the above structure, the crankshaft 4
Is divided into a motor-side crankshaft 42 and a cylinder-side crankshaft 43 that are connected to the motor 2, and an eccentric pin portion 41 that fits into the roller 34 is formed on the cylinder-side crankshaft 43. A rotation transmission portion 44 extending radially outward is formed at an end portion of a side crankshaft 42 that is connected to the eccentric pin portion 41.
A long groove 45 extending outward in the radial direction is formed on one side of the rotation transmitting portion 44, and a pin 46 slidably engaged with the long groove 45 is projectingly provided on the other side of the rotation transmitting section 44. The shaft center O is eccentric with respect to the center S of the cylinder chamber 30 toward the high-pressure rotation region where the compression chamber 6 is smaller than the suction chamber 5.

Specifically, the motor side crankshaft 42
Has one end connected to the motor 2 and the other end integrally formed with the rotation transmitting portion 44 extending radially outward, and the radial outer end of the rotation transmitting portion 44 is directed toward the opposite motor side. The rotation transmitting portion 44 is provided by protruding the pin 46.
Are positioned within the roller 34. On the other hand, the cylinder side crankshaft 43 has one end bearing supported by the rear head 33 and the other end integrally formed with an eccentric pin portion 41 which fits in the roller 34. Causes the rotation transmitting portion 44 formed on the motor-side crankshaft 42 to be positioned inside the roller 34, so that the axial length is made shorter than that by the height of the roller 34,
Further, the long groove 45 for slidably engaging the pin 46 protruding from the rotation transmitting portion 44 is formed on the end surface of the eccentric pin portion 41 from the axial center S of the cylinder side crankshaft 43 to the eccentric pin portion 41. It is formed toward the eccentric direction.

The cylinder side crankshaft 43
Is arranged so that its axis S coincides with the center S of the cylinder chamber 30, and the motor-side crankshaft 42
With respect to the center S of the cylinder chamber 30
The compression chamber 6 is on the high pressure rotation region side where it is smaller than the suction chamber 5, that is, when it advances in the clockwise direction starting from the installation position of the blade 36, it is on the region side of 180 to 360 degrees (in the embodiment, the cylinder). 27 to the center S of the chamber 30
The motor 2 and the compression element 3 are arranged so as to be eccentric in the casing 1 so that the center of the motor 2 and the center S of the cylinder chamber 30 are displaced from each other. It is installed in.

The operation will be described with reference to FIGS. 2 to 5. First, as shown in FIG. 2, the projection is provided on the radially outer end of the rotation transmitting portion 44 of the motor side crankshaft 42. With the pin 46 directed toward the blade 36, and when the blade 36 and the rotating tip portion 44 are in a parallel state, the starting point of rotation of the motor-side crankshaft 42 is: In the eccentric pin portion 41 formed on the cylinder side crankshaft 43, the long groove 45 formed in the eccentric pin portion 41 extends in the eccentric direction,
Since the pin 46 is engaged with the long groove 45, the eccentric pin portion 41 facing the outer peripheral side end portion of the long groove 45.
When the position of the blade 36 is used as a reference, the tip P of the eccentric direction is positioned rearward of the blade 36 in the clockwise direction, and is positioned near the discharge port 37.

When the motor-side crankshaft 42 rotates 90 degrees starting from the position of the pin 46 shown in FIG. 2 by the rotational driving of the motor 2, as shown in FIG. The motor side crankshaft 4
The cylinder-side crankshaft 43 is arranged so that the shaft center O of the motor-side crankshaft 42 is eccentric to the center S of the cylinder chamber 30 on the high-pressure rotation region side, and the pin 46 is rotated. Driven rotation through
The eccentric pin portion 4 is rotated by an angle larger than the rotation angle (90 degrees) of the rotation transmitting portion 44.
1, the eccentric tip portion P rotates from the position shown in FIG. 2 to a position of 90 degrees with the position of the blade 36 as a reference, and the position of the pin 46 of the motor-side crankshaft 42 and the eccentric pin The eccentric tip portion P of the portion 41 is oriented in the direction of 90 degrees. At this time, the eccentric pin portion 41 rotates at an angle larger than 90 degrees even though the motor-side crankshaft 42 rotates 90 degrees. It rotates faster than the crankshaft 42.

Further, even when the motor-side crankshaft 42 rotates 90 degrees from the position of FIG. 3 and the pin 46 is positioned 180 degrees from the starting point, the eccentric pin portion 41 is not moved as shown in FIG. , The eccentric direction front end portion P rotates from the position shown in FIG. 3 to a position which advances in the clockwise direction from the position of 180 degrees with respect to the position of the blade 36. At this time, the motor side crankshaft 42 3 rotates 90 degrees from the state shown in FIG. 3, the eccentric pin portion 41 rotates at an angle larger than 90 degrees, so the eccentric pin portion 41 is rotated by the motor side crankshaft 42.
It spins faster than.

Therefore, when the compression chamber 6 is larger than the suction chamber 5, that is, in the low-pressure rotation region, the eccentric pin portion 41 is attached to the eccentric pin portion 41.
Therefore, the roller 34, which revolves with the rotation of the eccentric pin portion 41, also revolves faster than the rotation speed of the motor-side crankshaft 42.

On the other hand, the motor side crankshaft 42
However, when the pin 46 rotates 90 degrees from the position of FIG. 4 and rotates to the position of 270 degrees from the starting point, the cylinder side crankshaft 43 becomes the motor side crankshaft 4
Rotation angle of rotation transmission part 44 that rotates with 2 (90 degrees)
Since the eccentric pin portion 41 rotates at a smaller angle,
As shown in FIG. 5, 270 with reference to the position of the blade 36 from the position where the eccentric tip portion P is clockwise behind the position of 180 degrees with reference to the position of the blade 36 shown in FIG. It will rotate to the position of degree,
The position of the pin 46 of the motor-side crankshaft 42 and the eccentric direction tip portion P of the eccentric pin portion 41 are both 270.
It turns in the direction of degrees. At this time, the eccentric pin portion 41 rotates at an angle smaller than 90 degrees even though the motor-side crankshaft 42 rotates 90 degrees from the position shown in FIG. The portion 41 rotates slower than the crankshaft 42 on the motor side.

Further, even when the motor-side crankshaft 42 rotates 90 degrees from the position of FIG. 5 and returns to the starting point shown in FIG. 2, the cylinder-side crankshaft 43 has a rotation angle of the rotation transmitting portion 44. Since the eccentric pin portion 41 rotates at a small angle, the eccentric direction tip portion P rotates from the position shown in FIG. 5 to a position immediately before the position of the blade 36 in the clockwise direction. Although the side crankshaft 42 rotates 90 degrees from the state of FIG. 5, the eccentric pin portion 41 rotates at an angle smaller than 90 degrees, so that the eccentric pin portion 41 moves toward the motor side. It rotates slower than the crankshaft 42.

Therefore, when the compression chamber 6 becomes smaller than the suction chamber 5, that is, in the high pressure rotation region, the eccentric pin portion 41 is slower than the rotation speed of the motor side crankshaft 42. As the roller 34 rotates, the roller 34, which revolves with the rotation of the eccentric pin portion 41, also revolves slower than the rotation speed of the motor-side crankshaft 42.

From the above, as shown by the solid line in FIG. 6, the revolution speed ωb of the roller 34 in the high pressure rotation region becomes slower than the revolution speed ωa in the low pressure rotation region, and the roller 34 in the high pressure rotation region. As the revolution speed ωb of becomes slower,
The flow velocity of the high-pressure fluid discharged from the compression chamber 6 via the discharge port 37 can be reduced, whereby overcompression can be reduced, the reduction in compression efficiency can be suppressed, and the revolution speed of the roller 34 in the high-pressure rotation region. Since ωb is slow and the revolution speed ωa in the low-pressure rotation region is fast, the compression power P2 obtained by the product of the compression load torque T and the revolution speed of the roller 34.
As shown by the solid line in FIG. 7, compared with the conventional one (P1) in which the revolution speed of the roller is constant, it can be reduced in the high-pressure rotation region and increased in the low-pressure rotation region. Power fluctuation can be reduced and vibration and noise can be suppressed.

In the embodiment, the rotation transmitting portion 44 formed on the motor-side crankshaft 42 is formed with the pin 46, and the eccentric pin portion 41 is formed with the long groove 45 for engaging the pin 46. A long groove may be formed in the rotation transmitting portion 44 and a pin may be formed in the eccentric pin portion 41.

In the above-described embodiment, the roller 34 is used.
Although it was made to revolve while rotating by the rotation of the eccentric pin portion 41 and brought into contact with the tip end portion of the blade 36, the roller 34 may be non-rotating as shown in FIG.

That is, the rotary compressor shown in FIG. 8 is different from the above-mentioned embodiment only in the rotating mechanism of the roller 34, and the structure of the crankshaft 4 is the same as that of the above-mentioned embodiment. The shaft 4 is divided into a motor-side crank shaft 42 and a cylinder-side crank shaft 42. Specifically, the rotating mechanism of the roller 34 will be described.
Outer peripheral cylindrical surface 34 of roller 34 installed in cylinder chamber 30
The blade 36 is integrally formed on the a, and the projecting tip side of the blade 36 is freely moved into and out of the receiving groove 71 of the rocking body 7 that is rotatably supported in the support hole 38 provided outside the cylinder chamber 30. And the roller 34 is configured as a non-rotating type that does not rotate together with the rotation of the eccentric pin portion 41 formed on the cylinder side crankshaft 43.

By doing so, as in the first embodiment, the roller 34 is made to rotate and the blade 36 is rotated.
The outer peripheral cylindrical surface 3 of the roller 34, which occurs when the structure is configured to contact the outer peripheral cylindrical surface 34a of the roller 34,
High pressure fluid can be prevented from leaking from the compression chamber 6 to the suction chamber 5 through the gap between the blade 4a and the blade 36, and the volumetric efficiency can be improved.

[0030]

As described above, according to the first aspect of the present invention, the revolution speed of the roller 34 in the high pressure rotation region can be made slower than the revolution speed in the low pressure rotation region, so the roller 34 in the high pressure rotation region. The flow velocity of the high-pressure fluid discharged from the compression chamber 6 can be reduced by the amount of the decrease in the rotation speed of, and thus overcompression can be reduced and reduction in compression efficiency can be suppressed.

Moreover, since the revolution speed of the roller 34 in the high-pressure rotation region can be slowed down and the revolution speed in the low-pressure rotation region can be increased, the compression power obtained by the product of the compression load torque and the revolution speed of the roller 34 is In comparison with the conventional one in which the revolution speed is constant, it can be reduced in the high-pressure rotation region and increased in the low-pressure rotation region, so that power fluctuation can be reduced and vibration and noise can be suppressed.

Further, according to the second aspect of the present invention, since the high pressure fluid can be prevented from leaking from the compression chamber 6 to the suction chamber 5 by utilizing the structure in which the roller 34 is non-rotating, the volumetric efficiency is improved. It can also be achieved.

[Brief description of drawings]

FIG. 1 is a partially cutaway sectional view of a rotary compressor according to the present invention.

FIG. 2 is an operation explanatory view of the rotary compressor according to the present invention.

FIG. 3 is an operation explanatory view of the rotary compressor according to the present invention.

FIG. 4 is an operation explanatory view of the rotary compressor according to the present invention.

FIG. 5 is an operation explanatory view of the rotary compressor according to the present invention.

FIG. 6 is a characteristic chart of the revolution speed and torque of the roller with respect to the rotation angle of the crankshaft, for explaining the effect of the present invention in comparison with a conventional example.

FIG. 7 is a characteristic diagram of compression power with respect to a rotation angle of a crankshaft, which illustrates the same effect and effect in comparison with a conventional example.

FIG. 8 is another embodiment of the rotary compressor according to the present invention.

FIG. 9 is a sectional view of a conventional rotary compressor.

[Explanation of symbols]

 2 motor 3 compression element 30 cylinder chamber 31 cylinder 34 roller 34a outer peripheral cylinder surface 36 blade 4 crankshaft 41 eccentric pin portion 42 motor side crankshaft 43 cylinder side crankshaft 44 rotation transmission portion 45 long groove 46 pin 5 suction chamber 6 compressor Chamber 7 Oscillator O Center of motor side crank shaft S Center of cylinder chamber

Claims (2)

[Claims] 1. A motor 2 and a compression element 3, which are fitted into a cylinder 31 having a cylinder chamber 30 in the compression element 3 and an eccentric pin portion 41 of a crankshaft 4 connected to the motor 2, Roller 34 revolving inside the cylinder chamber 30
And a blade 36 that divides the inside of the cylinder chamber 30 into a suction chamber 5 and a compression chamber 6, the motor-side crankshaft 4 connected to the motor 2.
2 and the cylinder side crank shaft 43 are formed separately, and the cylinder side crank shaft 43 is formed with an eccentric pin portion 41 that fits in the roller 34.
The rotation transmitting portion 44 extending outward in the radial direction is formed at the end of the connecting side shaft of the second eccentric pin portion 41 to the eccentric pin portion 4.
1 and the rotation transmission portion 44, a long groove 45 extending outward in the radial direction is formed, and a pin 46 slidably engaged with the long groove 45 is projectingly provided on the other side, while the motor-side crank The axis O of the shaft 42 is set to the center S of the cylinder chamber 30.
On the other hand, the rotary compressor is characterized in that the compression chamber 6 is eccentric to the high pressure rotation region side which is smaller than the suction chamber 5. 2. An oscillating body 7 for projecting a blade 36 on an outer peripheral cylindrical surface 34a of a roller 34 and rotatably supporting a protruding tip side of the blade 36 to the outside of a cylinder chamber 30.
The rotary compressor according to claim 1, wherein the roller 34 is configured to be non-rotating so as to be freely engaged with and retracted from the roller.