JPH11257264A - Helical blade type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the rotation mass of a rotor, and materialize a plan for making compression capacity greater without impairing manufacturing properties. SOLUTION: This compressor is equipped with a fixed cylindrical body 11, a cylinder 12 which is disposed thereto, and is formed out of a cylindrical body, in which one end side is blocked, the other end is opened, and the outer circumferential surface of the cylindrical body is covered, a blade 25 in a spiral shape to be interposed between the outer circumferential surface of the cylindrical body and the inner circumferential surface of the cylinder 12, and with a compression chamber 26 which is formed among the outer circumferential surface of the cylindrical body, the inner circumferential surface of the cylinder and the blade 25, and the eccentric rotation of the cylinder 12 with respect to the cylinder body 11 allows refrigerant gas to be introduced in the compression chamber, and thereby allows it to be compressed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor constituting, for example, a refrigeration cycle of an air conditioner, and more particularly to a helical blade type compressor.

[0002]

2. Description of the Related Art In recent years, for example, a helical blade type compressor has been proposed as a compressor constituting a refrigeration cycle of an air conditioner. According to this type of compressor, it is possible to eliminate the poor sealing performance of a conventional reciprocating compressor or a rotary compressor, improve the sealing performance with a relatively simple configuration, achieve efficient compression, and reduce the number of parts. Manufacturing and assembly are facilitated.

The helical blade type compressor has two specific configurations. One of them accommodates an eccentrically rotating roller in a fixed cylinder, forms a spiral groove on the outer peripheral surface of this roller, engages the blade, and engages a compression chamber formed between the cylinder, roller and blade. In this configuration, a refrigerant gas, which is a fluid to be compressed, is introduced and compressed.

On the other hand, a roller is disposed eccentrically in a rotating cylinder, a spiral groove is formed on the outer peripheral surface of the roller, a blade is engaged, and the roller is rotated in synchronization with the rotation of the cylinder. In this configuration, a refrigerant gas is introduced into a compression chamber formed between the roller and the blade and compressed.

[0005]

However, in the former configuration, since the roller, which is a rotating body, is provided with a spiral groove in which the blade is engaged, the roller becomes thicker, and the rotating mass of the roller increases. Therefore, the thickness of the cylinder accommodating the rollers is also increased, which increases the cost of parts and increases the weight of the compressor itself.

[0006] In the latter configuration, the roller, which is a rotating body that rotates in synchronization with the cylinder, is provided with a helical groove in which the blade is engaged, so that the roller becomes thick and the rotating mass of the roller increases. Therefore, the thickness of the cylinder also increases, which increases the cost of parts and increases the weight of the compressor itself.

[0007] Further, in this type of helical blade type compressor, particularly, a large compression capacity is required. However, if the size is increased in order to achieve a large capacity, the arrangement space of the counter balancer corresponding to the mass of the roller becomes a problem, and if high-speed rotation is performed using an inverter, vibration increases due to bending of the rotating shaft, Premature bearing wear and damage effects.

Therefore, it is desired to reduce the thickness of the roller, which is a rotating body, to reduce the rotating mass in any structure. However, a structure in which a spiral groove is provided here is adopted. As long as the request is not satisfied.

It is conceivable that a spiral groove is provided on the inner peripheral surface of the fixed cylinder to make the roller which is a rotating body a thin cylindrical body. However, the cylinder itself is a thin cylindrical body. It is extremely difficult to provide a spiral groove on this inner peripheral surface.

The present invention has been made in view of the above circumstances, and has as its object to reduce the rotating mass of a rotating body and achieve a large compression capacity without impairing manufacturability. Helical blade type compressor.

[0011]

According to a first aspect of the present invention, there is provided a helical blade type compressor in which a fixed cylindrical body, one end is closed, and the other end is opened. A cylinder formed of a cylindrical body and disposed so as to cover the outer periphery of the cylindrical body, a helical blade interposed between an outer peripheral surface of the cylindrical body and an inner peripheral surface of the cylinder, and the cylindrical body A compression chamber formed between the outer peripheral surface of the cylinder, the inner peripheral surface of the cylinder, and the blade, and eccentrically rotating the cylinder with respect to the cylindrical body to guide the fluid to be compressed into the compression chamber and compress the fluid. It is characterized by doing.

According to a second aspect of the present invention, in the helical blade type compressor according to the first aspect, the cylindrical body pivotally supports a rotating shaft that penetrates both ends of the cylindrical body and has an end connected to the cylinder.
The cylinder is eccentrically rotated by rotationally driving the rotation shaft.

[0013] Claim 3 is Claim 1 and Claim 2
In the helical blade type compressor according to any one of the above, the rotating shaft has a crank hole portion eccentric to a part thereof, and a drive shaft that engages with the crank hole portion on a closed surface of the cylinder is protruded, The cylinder is eccentrically rotated through the crank hole and the drive shaft as the rotation shaft rotates.

According to claim 4, claims 1 and 2
In the helical blade type compressor according to any one of the above, the rotating shaft has a crank part eccentric to a part thereof,
A bearing portion for pivotally supporting the crank portion is integrally provided on a closed surface of the cylinder, and the cylinder is eccentrically rotated via the crank portion and the bearing portion as the rotary shaft rotates.

According to a fifth aspect of the present invention, in the helical blade type compressor according to the first aspect, a compression mechanism is constituted by the cylindrical body, the cylinder, the blade, and the like. Is characterized in that a frame is integrally provided, and the frame is fixedly supported by the case.

According to a sixth aspect of the present invention, in the helical blade type compressor according to the fifth aspect, the frame partitions the inside of the case into a high pressure side and a low pressure side. According to a seventh aspect of the present invention, in the helical blade type compressor according to the sixth aspect, the compression mechanism portion including the cylindrical body, the cylinder, and the blade is disposed on the high pressure side in the case, and the cylinder has a peripheral portion on the opening end side. A flange is provided integrally along the portion, and the flange surface is a thrust surface.

According to an eighth aspect of the present invention, in the helical blade type compressor according to the sixth aspect, a compression mechanism portion comprising the cylindrical body, the cylinder and the blade is disposed on a low pressure side in a case, and the cylinder is a cylinder cover. It is characterized by being covered.

According to a ninth aspect of the present invention, there is provided a helical blade type compressor comprising a fixed cylindrical body and a cylindrical body closed at one end and opened at the other end. A movable cylinder disposed so as to cover the outer periphery of the cylindrical body, a fixed cylinder which is formed of a tubular body having one end closed and the other end side opened, and disposed so as to cover the outer periphery of the movable cylinder; A helical inner blade interposed between the outer peripheral surface of the cylindrical body and the inner peripheral surface of the movable cylinder; and a helical inner blade formed between the outer peripheral surface of the cylindrical body, the inner peripheral surface of the movable cylinder, and the inner blade. A spiral outer blade interposed between an outer peripheral surface of the movable cylinder and an inner peripheral surface of the fixed cylinder; an outer peripheral surface of the movable cylinder, an inner peripheral surface of the fixed cylinder, and the outer blade. Between An outer compression chamber made, by eccentrically rotating the movable cylinder relative to the cylinder, characterized by compressing leading the compressed fluid, each said inner compression chamber and an outer compression chamber.

According to a tenth aspect, in the helical blade type compressor according to the ninth aspect, the cylindrical body pivotally supports a rotating shaft penetrating both ends thereof, and the rotating shaft partially includes an eccentric crank portion, A bearing portion for pivotally supporting the eccentric crank portion is integrally provided on the closing surface of the cylinder, and the movable cylinder is eccentrically rotated via the eccentric crank portion and the bearing portion with the rotation of the rotating shaft. I do.

According to an eleventh aspect of the present invention, in the helical blade type compressor according to any one of the ninth and tenth aspects, the inner blade and the outer blade are about 18
It is characterized by being arranged at a position shifted by 0 degrees.

According to a twelfth aspect, in the helical blade compressor according to any one of the ninth to eleventh aspects, the inner blade and the outer blade have the same suction amount of the fluid to be compressed in the inner compression chamber and the outer compression chamber. The pitch or helix angle of each other is formed to be the same.

According to a thirteenth aspect, in the helical blade type compressor according to any one of the ninth to eleventh aspects, the movable cylinder is provided with a balance hole communicating the inner compression chamber and the outer compression chamber. It is characterized by being able to.

According to a fourteenth aspect, in the helical blade compressor according to any one of the ninth and tenth aspects, the upper surface of the cylindrical body or the movable cylinder closing surface is a thrust surface.

According to a fifteenth aspect, in the helical blade type compressor according to the ninth to fourteenth aspects, the inner blade is engaged with a spiral groove provided on the outer peripheral surface of the cylindrical body, and the outer blade is connected to a fixed cylinder. It is characterized by being engaged with a spiral groove provided on the inner peripheral surface.

According to a sixteenth aspect of the present invention, in the helical blade type compressor according to the ninth to fourteenth aspects, the inner blade is engaged with a spiral groove provided on an outer peripheral surface of a cylindrical body, and the outer blade is a movable cylinder. It is characterized by being engaged with a spiral groove provided on the outer peripheral surface.

According to a seventeenth aspect, in the helical blade type compressor according to the ninth to fourteenth aspects, the inner blade is engaged with a helical groove provided on the inner peripheral surface of the movable cylinder, and the outer blade is movable. Characterized by being engaged with a spiral groove provided on the outer peripheral surface.

According to an eighteenth aspect of the present invention, in the helical blade type compressor according to any one of the ninth to fourteenth aspects, the inner blade is engaged with a helical groove provided on the inner peripheral surface of the movable cylinder, and the outer blade is fixed cylinder. Characterized in that it is engaged with a spiral groove provided on the inner peripheral surface of the.

According to the first aspect of the present invention, by adopting the means for solving such a problem, the rotating mass of the rotating body can be reduced to increase the capacity. In the second invention, the rotating mass of the rotating body can be reduced to achieve a large capacity, and the compression capacity due to the two cylinders can be further increased.

[0029]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 shows a helical blade type compressor of the first invention. The compressor has a compression mechanism 3 connected to a closed case 1 via a rotary shaft 2.
And the motor unit 4 is accommodated.

The compression mechanism 3 is disposed on the upper side, and the motor 4 is disposed on the lower side. A part of the rotating shaft 2 protrudes further downward from the lower end of the electric motor unit 4, and is immersed in the lubricating oil of an oil sump 5 formed at the inner bottom of the sealed case 1.

A discharge refrigerant pipe 6 is connected to the upper part of the closed case 1 and a suction refrigerant pipe 7 is connected to the middle part.
Is connected. A condenser 8, an expansion valve 9, and an evaporator 10 are sequentially connected from the discharge refrigerant pipe 6 to the suction refrigerant pipe 7, and these constitute, for example, a refrigeration cycle of an air conditioner.

Next, the compression mechanism 3 will be described in detail. In the figure, reference numeral 11 denotes a cylindrical body having an upper portion having a small diameter and a lower portion having a large diameter, and a peripheral surface and an upper end surface of the small diameter portion 11a are covered by a cylinder 12 described later. The large-diameter portion (hereinafter, referred to as a frame) 11b is disk-shaped, and has a diameter substantially equal to the inner diameter of the closed case 1 and is fitted to the inner peripheral surface of the closed case 1 so that the closed case 1 It is attached and fixed to the closed case 1 by welding means from the outer peripheral side. That is, the frame 11b partitions the inside of the sealed case 1 up and down.

A part of the lower end surface of the frame 11b protrudes downward. A pivot hole 13 is provided along the central axis of the cylindrical body 11 including the protrusion, and the main shaft 2a of the rotary shaft 2 is inserted. And it is pivoted freely.

At the upper end of the pivot hole 13, a concave eccentric bearing 14 is provided. The rotating shaft main shaft portion 2a
A crank portion 2b eccentric to the center axis of the main shaft portion 2a is integrally connected to an upper end of the main shaft portion 2a, and is pivotally supported by the eccentric bearing portion 14.

The cylinder 12 has an open lower surface and is formed in a substantially hat shape in cross section. The dimension from the inside of the upper closed surface 12a to the lower surface of the lower flange 12b, which is the depth dimension, is the same as that of the cylindrical body. It is slightly larger than the height of the small diameter portion 11a. Therefore, the cylinder 12 is mounted on the cylindrical small diameter portion 1.
With the cover 1a covered, the lower surface of the flange 12b rests on the upper surface of the cylindrical frame 11b.

A mounting hole 12c with which the drive shaft 15 is engaged is provided at the center of the cylinder closing surface 12a. The drive shaft 15 has a flange 15a at an upper end thereof resting on the cylinder closing surface 12a, and a shaft 15 integrated with the flange 15a.
b protrudes into the cylinder 12. In other words, the drive shaft 15 is hung on the cylinder closing surface 12a.

The shaft portion 15a of the drive shaft 15 is rotatably supported by a crank hole 16 provided from the upper end surface of the rotary shaft crank portion 2b. For this reason, the rotation of the rotary shaft 2 pivotally supported by the cylindrical body 11 causes the cylinder 12 to eccentrically rotate via the rotary shaft crank portion 2b and the drive shaft 15. And the cylinder flange 12
b From where the lower surface rests on the upper surface of the cylindrical frame 11b,
The lower surface of the cylinder flange 12b serves as a thrust surface and slides on the frame 11b.

A seal ring groove 18 is formed on the upper surface of the cylindrical small-diameter portion 11a and along the periphery of the eccentric bearing portion 14 with which the seal ring 17 is engaged. The seal ring 17 protrudes from the upper end surface of the cylindrical small diameter portion 11a,
It comes into contact with the cylinder closing surface 12a and forms a seal for the inside and the outside.

When the cylinder 12 rotates eccentrically, a pin 20 is provided on the upper surface of the cylindrical frame 11b by selecting a position where the cylinder flange 12b does not contact. On the other hand, a pin 21 is also provided at a position near the pin 20 on the cylinder flange 12b, and an arm 22 is bridged between the pins 20, 21 to constitute a rotation stopping mechanism 23. That is, the eccentric rotation of the cylinder 12 accompanying the rotation of the rotary shaft 2 is allowed to rotate, and the rotation is prevented.

On the peripheral surface of the cylindrical small diameter portion 11a, a spiral groove 24 whose pitch becomes gradually smaller is provided from the lower side to the upper side. A spiral blade 25 is engaged with the spiral groove 24 so as to be able to freely enter and exit.

The blade 25 is formed of, for example, a fluororesin material, and an extremely smooth material is selected. This inner diameter is formed larger than the diameter of the cylindrical small diameter portion 11a, and is fitted into the spiral groove 24 in a state where the diameter is forcibly reduced. As a result, the outer peripheral surface of the blade 25 bulges and deforms so that the outer peripheral surface is always in elastic contact with the inner peripheral surface of the cylinder 12 in a state where the blade 25 is assembled into the cylinder 12 together with the small-diameter portion 11 a of the cylindrical body.

Then, with the eccentric rotation of the cylinder 12, the rolling contact portion between the inner peripheral surface of the cylinder 12 and the cylindrical small diameter portion 11a gradually moves along the circumferential direction of the cylindrical small diameter portion 11a. The blade 25 is immersed in the spiral groove 24 as the rolling contact portion approaches, and the outer peripheral surface of the blade 25 is completely flush with the peripheral surface of the cylindrical small diameter portion 11a at a position facing the rolling contact portion. .

When the rolling contact portion passes, the blade 25 protrudes from the spiral groove 24 according to the distance from the rolling contact portion. Is maximized. Thereafter, since the vehicle approaches the rolling contact portion again, the above-described operation is repeated.

Further, the cylindrical small diameter portion 11a and the cylinder 12
When the cylinder 12 is eccentrically covered with respect to the cylindrical body small-diameter portion 11a, and the cylindrical body small-diameter portion 1
Since the inner peripheral portion of the cylinder 12 is in a rolling contact state with a part of the peripheral surface of the cylinder 1a, the cylindrical small-diameter portion 11a and the cylinder 12
A crescent-shaped space is formed between the inner peripheral surface and the inner peripheral surface.

When this space is viewed along the axial direction, the blade 25 is engaged with the spiral groove 24 and the cylindrical small-diameter portion 11a
Since the inner peripheral portion of the cylinder 12 is in rolling contact with the peripheral surface, the blade 2 is located between the cylindrical small diameter portion 11a and the inner peripheral surface of the cylinder 12.
5 divides the space into a plurality of continuous spaces. These spaces are referred to as compression chambers 26. From the setting of the pitch of the spiral groove 24, the volume of each compression chamber 26 gradually decreases from the lower compression chamber 26 to the upper compression chamber 26.

On the other hand, an introduction guide port 27 is provided to penetrate the cylindrical body frame 11b over its upper and lower surfaces. As the position of the introduction guide port 27, a position that is not exposed to the outside even when the cylinder 12 rotates eccentrically is selected.

An outlet guide port 28 is provided on the cylinder closing surface 12a, and communicates the uppermost end compression chamber 26 inside the closing surface 12a and the inside of the closed case 1 outside the closing surface 12a.

The cylinder frame 11b has a cylinder 12
An oil return hole 30 is provided through the upper and lower surfaces of the frame 11b by selecting a position that is not covered by the flange portion 12b even if the eccentric rotation occurs. An oil pipe 31 projects from the lower end of the rotating shaft 2 immersed in the lubricating oil in the oil reservoir 5. An oil hole 32 having substantially the same diameter as the oil pipe 31 is provided along the axis of the rotary shaft main shaft portion 2a, and communicates with the oil pipe 31.

An intermediate portion of the oil hole 32 and the peripheral surface of the rotary shaft main shaft portion 2a are communicated with each other by an oil guide horizontal hole 33. And
An oil discharge lateral hole 34 in which the oil guide lateral hole 33 intermittently opposes with the rotation of the rotating shaft 2 is provided in the cylindrical body small diameter portion 11a.
It is provided penetrating from the peripheral surface of the pivot hole 13 to the peripheral surface of the small diameter portion 11a.

The upper end of the oil hole 32 extends to a position near the crank hole 16 provided in the rotary shaft crank portion 2b. The upper end of the oil hole 32 and the crank hole 16 are formed by a small-diameter oil guide hole 35. Communicated.

The rotating shaft main shaft portion 2a is provided with a cylindrical body support hole 13
An oil groove 36 is provided in a spiral shape on the peripheral surface of the portion pivotally supported by. An oil groove 37 is also spirally provided on the peripheral surface of the drive shaft 15 which engages with the rotary shaft crank hole 16.

The motor section 4 is opposed to a rotor 40 fitted to the rotating shaft main shaft section 2a with a narrow gap on the peripheral surface of the rotor 40, and fitted to the inner peripheral surface of the closed case 1. And a stator 41 to be used.

This is a helical blade type compressor configured as described above, and energizes the electric motor unit 4 to rotate the rotary shaft 2 together with the rotor 40 integrally. The torque of the rotating shaft 2 is transmitted to the cylinder 12 via the crank 2b and the drive shaft 15. Since the rotation stopping mechanism 23 operates to restrict the rotation of the cylinder 12, the cylinder 12 makes a revolving motion of eccentric rotation.

With the eccentric rotation of the cylinder 12, the rolling contact position of the cylinder 12 with respect to the peripheral surface of the cylindrical small diameter portion 11a gradually moves in the circumferential direction, and the blade 25 moves in and out of the helical groove 24. The small-diameter portion 11a moves in the radial direction.

By a series of these operations, low-pressure refrigerant gas is sucked from the evaporator 10 into the closed case 1 through the suction refrigerant pipe 7. Inside the sealed case 1 is a cylindrical frame 1
1b, a low-pressure chamber 42 filled with a low-pressure gas is formed in the lower portion of the closed case 1 from where the suction refrigerant pipe 7 is connected to the lower portion.

The refrigerant gas filling the low-pressure chamber 42 is guided to the lowermost compression chamber 26 via the introduction guide port 27. Then, as the cylinder 12 rotates eccentrically, it is sequentially transferred to the compression chamber 26 on the upper side.

Since the volume of each of the compression chambers 26 is gradually reduced from the lower side to the upper side, the refrigerant gas is compressed while being sequentially transferred through each of the compression chambers 26, and the uppermost end of the compression chamber 2 is compressed.
At 6, the pressure is increased to a predetermined pressure.

The high-pressure gas in the compression chamber 26 is discharged into the closed case 1 through the outlet guide port 28. That is, the high-pressure gas fills the upper chamber of the closed casing 1 partitioned by the cylindrical frame 11b, and this is called the high-pressure chamber 43.

In other words, the cylindrical frame 11b partitions the inside of the sealed case 1 into a low-pressure chamber 42 and a high-pressure chamber 43, and the electric motor unit 4 is located in the low-pressure chamber 42 and the compression mechanism unit 3
Are located in the high-pressure chamber 43. In addition, since the refrigerant discharge pipe 6 communicates with the high-pressure chamber 43, the high-pressure gas filling the high-pressure chamber 43 is discharged from the refrigerant discharge pipe 6 to the condenser 8, and a well-known refrigeration cycle operation is performed.

With the eccentric rotation of the cylinder 12, the high pressure gas filling the high pressure chamber 43 causes the cylinder flange 12b
Is pressed against the disc-shaped frame 11b, and the cylinder flange 1
The lower surface 2b serves as a thrust surface and slides on the frame 11b.

With the rotation of the rotating shaft 2, the lubricating oil in the oil reservoir 5 is sucked up from the oil pipe 31 and led to the oil hole 32 and the like.
For example, oil is supplied to the respective sliding contact surfaces such as the rotary shaft main shaft portion 2a and the cylindrical body support hole portion 13 to ensure smooth movement of these portions. The lubricating oil after refueling is returned to the oil reservoir 5 again, and circulates in the above-described path.

According to such a helical blade type compressor, the cylinder 12 is a rotating body, and the blade 2
5 is not provided with the spiral groove 24 to be engaged,
The thickness of the cylinder 12 can be made extremely thin within the range of the strength and rigidity, so that the rotating mass is reduced, and the unbalanced mass that causes vibration is reduced.

That is, even if the compression capacity of the helical blade type compressor is increased, a large unbalance is unlikely to occur, and the vibration is small and the reliability is improved.

In the above configuration, the cylindrical frame 1
1b, the compression mechanism 3 is disposed on the upper side, and the electric motor 4 is disposed on the lower side. However, the present invention is not limited to this.
As shown in (1), the compression mechanism 3 may be arranged on the lower side of the cylindrical body frame 11b, and an electric motor (not shown) may be arranged on the upper side.

In this configuration, the cylinder frame 11b is provided integrally with the cylinder cover 11A to cover the cylinder 12. The cylinder cover 11A is immersed in the lubricating oil in the oil reservoir 5, but it prevents the lubricating oil from being agitated due to the eccentric rotation of the cylinder 12, and converts the high-pressure gas discharged from the discharge guide port 28 into the lubricating oil. It also has a muffler effect when it is guided from the high pressure chamber 43, which is the upper space of the frame 11b, while being isolated from the frame 11b.

The following helical blade type compressor can be employed without changing the basic configuration. That is, here, a helical blade type compressor having two cylinders will be described.

As shown in FIG. 3, the compression mechanism 3A is arranged on the lower side, and the motor unit 4 is arranged on the upper side, and these are connected to each other via a rotating shaft 2A. In the compression mechanism 3A, the main shaft 2a of the rotating shaft 2A is pivotally supported by a pivot hole 13 provided along the axis of the cylindrical body 11B.

The cylindrical frame 11b is attached and fixed to the inner peripheral portion of the closed case 1, and partitions the inside of the closed case up and down. The small-diameter portion 11a of the cylindrical body 11B is located on the lower side of the frame 11b, and a first spiral groove 24A is provided on this peripheral surface. The pitch of the first spiral groove 24A is reduced from the upper side to the lower side, and the inner blade 25A is engaged.

The movable cylinder 12A is arranged so as to cover the peripheral surface and lower surface of the cylindrical small-diameter portion 11a, and the fixed cylinder 1 is further covered so as to cover the peripheral surface and lower surface of the movable cylinder 12A.
2B are arranged. In other words, the movable cylinder 12A is interposed between the cylindrical body 11B and the fixed cylinder 12B.

The upper end of the fixed cylinder 12B is open, and a flange 12c is integrally provided along the outer circumference thereof, and is fixed to the cylindrical body frame 11b via the fixture 45. And, a concave thrust receiving portion 46 is provided along the periphery of the upper end opening of the fixed cylinder 12B,
A locking flange 12d provided along the periphery of the upper end opening of the movable cylinder 12A is supported.

At the lower end of the rotary shaft main shaft portion 2a, a crank portion 2c eccentric to the center shaft is integrally provided.
The movable cylinder 12A is rotatably supported by a bearing 47 provided on the lower end closing surface 12e.

The movable cylinder 12A and the cylindrical body 11
A, or between the movable cylinder 12A and the fixed cylinder 12B, is provided with a rotation stopping mechanism (not shown) for restricting the rotation of the movable cylinder 12A and allowing the revolution.

As a result, the movable cylinder 12A rotates eccentrically via the crank portion 2c with the rotation of the rotary shaft 2. The movable cylinder 12A has a cylindrical body 1 with a part of its inner peripheral surface.
1B, and a part of the outer peripheral surface 180 degrees opposite to the contact part is fixed cylinder 12B.
Contacts a part of the inner peripheral surface.

A second spiral groove 24B is provided on the inner peripheral surface of the fixed cylinder 12B, and the outer blade 25B is engaged with the second spiral groove 24B. Like the first spiral groove 24A, the second spiral groove 24B also has a gradually smaller pitch from the upper side to the lower side, and is designed to have the same pitch or spiral angle. I have.

The cylindrical small diameter portion 11a and the movable cylinder 12A
The inner compression chamber 26A is formed by the inner cylinder 25A and the inner blade 25A, and the outer compression chamber 26B is formed by the movable cylinder 12A, the fixed cylinder 12B, and the outer blade 25B.

The suction refrigerant pipe 7 penetrates through the closed case 1 and is inserted and fitted into the introduction guide hole 48 provided from the peripheral surface of the cylindrical body frame 11b toward the center axis. The insertion end face of the suction refrigerant pipe 7 is provided with an introduction guide hole 48.
And a suction guide port 49 communicating with the gap and the inner and outer compression chambers 26A and 26B.

An outlet guide port 50 is provided on the lower end closed surface 12e of the movable cylinder 12A, while a first outlet guide hole 51 is provided through the lower peripheral wall of the fixed cylinder 12B. One end is fitted.

The lead-out guide pipe 52 is bent in an L-shape, and the other end of the rising end is a second lead-out guide provided to penetrate vertically through the cylindrical frame 11b and the fixed cylinder mounting flange 12c. The holes 53 are fitted. Therefore, the outer compression chamber 26 </ b> B and the inside of the upper side closed case 1 of the cylindrical body frame 11 b communicate with each other through the guide pipe 52.

An oil pipe 31 protrudes from the lower surface of the rotary shaft crank portion 2c, and protrudes downward through a hole 54 provided in the lower closed surface 12f of the fixed cylinder 12B. The rotary shaft 2A is provided with an oil guide path (not shown) that communicates with the oil pipe 31. With the rotation of the rotary shaft 2A, the lubricating oil in the oil reservoir 5 can be sucked up and supplied to each sliding portion. It has become.

A discharge refrigerant pipe 6 is connected to the upper end of the closed case 1, and a refrigeration cycle communicating with the suction refrigerant pipe 7 via the condenser 8, the expansion valve 9, and the evaporator 10 is formed. The electric motor unit 4 includes a rotor 40 fitted to the rotating shaft 2A, and a stator 41 opposed to the outer peripheral surface with a small gap and fitted to the inner peripheral surface of the sealed case 1. You.

When the electric motor 4 is energized and the rotary shaft 2A is driven to rotate, the crank 2c rotates eccentrically, causing the movable cylinder 12A to eccentrically rotate. In the movable cylinder 12A, a portion that is 180 degrees opposite to the inner peripheral surface and the outer peripheral surface is always in rolling contact with the peripheral surface of the cylindrical small-diameter portion 11a and the inner peripheral surface of the fixed cylinder 12B. The outer compression chambers 26A and 26B are shifted by 180 degrees from each other.

A low-pressure refrigerant gas is sucked into the compressor from the evaporator 10 through the suction refrigerant pipe 7 and directly through the suction guide port 49 to the inner compression chamber 26A and the outer compression chamber 26.
B and introduced.

Due to the structure and operation of the movable cylinder 12A, the low-pressure gas is alternately introduced into the inner compression chamber 26A and the outer compression chamber 26B, and the first and second spiral grooves 24A, 24B are provided.
Are equal in the pitch or the helical angle of the inner and outer compression chambers 26A and 26B.

The low-pressure gas is compressed as it is transferred from the upper side to the lower side of each of the compression chambers 26A, 26B, and is increased to a predetermined pressure in the lowermost compression chambers 26A, 26B.
The high-pressure gas in the inner compression chamber 26A is led out from the outlet guide port 50 to the outside of the movable cylinder 12A, and the outer compression chamber 26B
Merges with the high-pressure gas derived from

The combined high-pressure gas is led to the lead-out guide pipe 52 and is led out from the open end. That is, the cylindrical body frame 11 from which the lead-out guide pipe 52 is opened
It is led out to the high-pressure chamber 43 on the upper side of b. The high-pressure gas once filled in the high-pressure chamber 43 is discharged from the discharge refrigerant pipe 6 and guided to the condenser 8 to constitute a refrigeration cycle.

If the helical blade type compressor having such a configuration is employed, a large compression capacity similar to that of a so-called two-cylinder can be obtained without increasing the size of the sealed case 1 so much. Moreover, the movable cylinder 12 which is basically a rotating body
The advantageous condition that the thickness of A can be reduced, the rotating mass does not increase, and the generation of vibration can be suppressed does not need to be changed.

A helical blade type compressor as shown in FIG. 4 may be used. Basically, there is no change in that a movable cylinder 12C described later is interposed between the cylindrical body 11B and the fixed cylinder 12B, and the eccentric rotation is performed. Therefore, the same components as those described above with reference to FIG. Are given the same numbers, and a new description is omitted.

The upper end of the movable cylinder 12C only needs to be open. Therefore, only the suction guide port 49 needs to be provided in the upper end opening of the fixed cylinder 12B, so that productivity can be improved and component material costs can be reduced as compared with the compressor described above.

Since the open end of the movable cylinder 12C as a gas introduction portion is surrounded by the fixed cylinder 12B on the low pressure side, no gas leak occurs. By providing the thrust receiver of the movable cylinder 12C at the opening end of the movable cylinder 12C and the lower end of the cylindrical body 11B, smooth eccentric rotation of the movable cylinder 12C is guaranteed.

The opening end of the movable cylinder 12C is opened so that the inner compression chamber 26A and the outer compression chamber 26B are connected, so that the efficiency of refrigerant gas suction can be improved. Further, since the plurality of balance holes 39 are provided on the peripheral wall of the movable cylinder 12C, the inner compression chamber 26A and the outer compression chamber 26B are communicated with the compression chambers having the same pressure. When an over-compression state occurs, the gas escapes to the other compression chamber, and pressure can be made uniform.

The movable cylinder 12 described above
A to 12C are characterized in that all of the spiral grooves 24A and 24B are not provided, but the present invention is not limited to this, and a configuration in which spiral grooves are provided as described below may be employed.

As shown in FIG. 5, the spiral groove 24A with which the inner blade 25A engages is provided on the peripheral surface of the cylindrical small diameter portion 11B, but the spiral groove 24B with which the outer blade 25B engages. Is provided on the outer peripheral surface of the movable cylinder 12D.

Therefore, since it is not necessary to provide the fixed cylinder 12E with any spiral groove, the thickness can be reduced. The spiral groove 2 is formed on the outer peripheral surface of the movable cylinder 12D.
Since the 4B is provided, the number of man-hours can be easily reduced as compared with the process of providing the spiral groove 24B on the inner peripheral surface of the fixed cylinder 12B as described with reference to FIGS.

As shown in FIG. 6, each of the cylindrical body 11C and the fixed cylinder 12E does not have a spiral groove, and instead has the inner blade 25 on the inner peripheral surface of the movable cylinder 12F.
A first helical groove 24A with which A engages is provided, and a second helical groove 24B with which the outer blade 25B engages is provided on the outer peripheral surface.

In this case, the first and second spiral grooves 24A,
Naturally, the phases are shifted so that the outer cylinder 24B does not interfere with the inner and outer diameters of the movable cylinder 12F. As a result, although the movable cylinder 12F becomes thicker than that described above, the two spiral grooves 24A and 24B are provided here. The influence of an increase in weight can be suppressed as much as possible by providing the, and an increase in the rotating mass can be prevented.

FIG. 7 shows the first and second spiral grooves 24A, 24A.
The movable cylinder 12F provided with the compression mechanism 4B and the entire compression mechanism 3B are shown. The same parts as those described above are denoted by the same reference numerals, and a new description will be omitted.

The fixed cylinder 12E can be made thinner, and since the cylindrical body 11C and the fixed cylinder 12E have no spiral groove, they can be integrally formed and concentrically machined to maintain high precision. In this case, the lower end of the fixed cylinder 12E is inevitably opened, but the lid 55 may be provided here and closed.

As shown in FIG. 8, a first spiral groove 25A for engaging the inner blade 24A is provided on the inner peripheral surface of the movable cylinder 12G, and the outer blade 24B is engaged on the inner peripheral surface of the fixed cylinder 12H. A second spiral groove 25B may be provided. In this case, the movable cylinder 12G and the fixed cylinder 1
Thickness of 2H and increase in weight can be suppressed as much as possible.

[0099]

As described above, according to the helical blade type compressor of the present invention, the rotating body is made thinner to reduce the rotating mass, and a large compression capacity can be realized without impairing the manufacturability. The effect is that it can be done.

[Brief description of the drawings]

FIG. 1 is a sectional view of a helical blade type compressor constituting a refrigeration cycle according to an embodiment of the first invention.

FIG. 2 is a cross-sectional view of a part of a compressor according to another embodiment.

FIG. 3 is a sectional view of a helical blade type compressor constituting a refrigeration cycle according to one embodiment of the second invention.

FIG. 4 is a cross-sectional view of a compression mechanism according to another embodiment.

FIG. 5 is a cross-sectional view of a part of a compression mechanism according to still another embodiment.

FIG. 6 is a cross-sectional view of a part of a compression mechanism according to still another embodiment.

FIG. 7 is a sectional view of the compression mechanism of the embodiment.

FIG. 8 is a cross-sectional view of a compression mechanism according to still another embodiment.

[Explanation of symbols]

 11 ... Cylinder, 12 ... Cylinder, 25 ... Blade, 26 ... Compression chamber, 3 ... Compression mechanism, 2 ... Rotating shaft, 12b ... Flange (of cylinder), 16 ... Crank hole, 15 ... Drive shaft, 2b ... Crank part, 14 ... Eccentric bearing part, 11b ... Frame, 43 ... High pressure chamber, 42 ... Low pressure chamber, 11A ... Cylinder cover, 11B ... Cylinder, 12A ... Movable cylinder, 12B ... Fixed cylinder, 24A ... First spiral 25A: inner blade, 26A: inner compression chamber, 24B: second spiral groove, 25B: outer blade, 26B: outer compression chamber.

Claims (18)

[Claims] 1. A fixed cylindrical body, one end of which is closed,
The other end side is formed of a cylindrical body having an opening, and a cylinder disposed so as to cover the outer periphery of the cylindrical body, and a helical shape interposed between an outer peripheral surface of the cylindrical body and an inner peripheral surface of the cylinder. A compression chamber formed between the outer peripheral surface of the cylindrical body, the inner peripheral surface of the cylinder, and the blade; and eccentrically rotating the cylinder with respect to the cylindrical body to cover the compression chamber. A helical blade type compressor which guides and compresses a compressed fluid. 2. The cylindrical body of claim 1, wherein said cylindrical body penetrates both ends and pivotally supports a rotating shaft whose end is connected to the cylinder, and drives said rotating shaft to rotate the cylinder eccentrically. The helical blade type compressor according to claim 1, wherein 3. The rotary shaft has an eccentric crank hole in a part thereof, and a drive shaft engaging with the crank hole is protrudingly provided on a closing surface of the cylinder. 3. The helical blade type compressor according to claim 1, wherein the cylinder is eccentrically rotated via the crank hole and the drive shaft. 4. The rotary shaft has a partially eccentric crank portion, and a bearing portion for pivotally supporting the crank portion is integrally provided on a closed surface of the cylinder. The helical blade type compressor according to any one of claims 1 and 2, wherein the cylinder is eccentrically rotated through a portion and a bearing portion. 5. A compression mechanism is constituted by the cylindrical body, the cylinder and the blade, and the compression mechanism is housed in a case. The frame is integrally provided with the cylinder, and the frame is attached to the case. The helical blade type compressor according to claim 1, wherein the compressor is fixedly supported. 6. The helical blade type compressor according to claim 5, wherein the frame partitions the inside of the case into a high pressure side and a low pressure side. 7. A compression mechanism comprising the cylindrical body, the cylinder and the blade is disposed on the high pressure side in the case, and the cylinder has a flange integrally provided along a peripheral portion on the opening end side. 7. The helical blade type compressor according to claim 6, wherein the flange surface is a thrust surface. 8. A compression mechanism comprising the cylinder, the cylinder and the blade is disposed on a low pressure side in the case.
The helical blade type compressor according to claim 6, wherein the cylinder is covered with a cylinder cover. 9. A fixed cylinder, a cylindrical body having one end closed and one end open, and a movable cylinder disposed so as to cover the outer periphery of the cylinder, one end closed, It consists of a cylindrical body whose other end is open,
A fixed cylinder disposed so as to cover the outer periphery of the movable cylinder, a spiral inner blade interposed between an outer peripheral surface of the cylindrical body and an inner peripheral surface of the movable cylinder, and an outer peripheral surface of the cylindrical body And an inner compression chamber formed between the inner peripheral surface of the movable cylinder and the inner blade, a helical outer blade interposed between the outer peripheral surface of the movable cylinder and the inner peripheral surface of the fixed cylinder, An outer compression chamber formed between the outer peripheral surface of the movable cylinder, the inner peripheral surface of the fixed cylinder, and the outer blade; and eccentrically rotating the movable cylinder with respect to the cylindrical body, thereby forming the inner compression chamber. A helical blade type compressor, wherein a fluid to be compressed is guided to each of the outer compression chamber and the outer compression chamber for compression. 10. The cylindrical body pivotally supports a rotating shaft penetrating both ends thereof, the rotating shaft partially having an eccentric crank portion, and the eccentric crank portion is pivotally mounted on a closed surface of the cylinder. The helical blade type compressor according to claim 9, wherein a bearing portion to be supported is provided integrally, and the movable cylinder is eccentrically rotated via the eccentric crank portion and the bearing portion as the rotation shaft rotates. 11. The helical blade type compressor according to claim 9, wherein said inner blade and said outer blade are arranged at positions shifted from each other by about 180 degrees. 12. The inner blade and the outer blade are formed to have the same pitch or the same spiral angle so that the amount of fluid to be compressed in the inner compression chamber and the outer compression chamber is the same. A helical blade type compressor according to any one of claims 9 to 11. 13. The helical blade type according to claim 9, wherein the movable cylinder is provided with a balance hole communicating the inner compression chamber and the outer compression chamber. Compressor. 14. The helical blade type compressor according to claim 9, wherein an upper surface of said cylindrical body or said movable cylinder closing surface is a thrust surface. 15. An inner blade is engaged with a spiral groove provided on an outer peripheral surface of a cylindrical body, and the outer blade is engaged with a spiral groove provided on an inner peripheral surface of a fixed cylinder. The helical blade type compressor according to any one of claims 9 to 14. 16. The method according to claim 16, wherein the inner blade is engaged with a spiral groove provided on the outer peripheral surface of the cylindrical body, and the outer blade is engaged with a spiral groove provided on the outer peripheral surface of the movable cylinder. The helical blade type compressor according to any one of claims 9 to 14. 17. The method according to claim 17, wherein the inner blade is engaged with a spiral groove provided on an inner peripheral surface of the movable cylinder, and the outer blade is engaged with a spiral groove provided on an outer peripheral surface of the movable cylinder. The helical blade type compressor according to any one of claims 9 to 14. 18. The method according to claim 18, wherein the inner blade is engaged with a spiral groove provided on an inner peripheral surface of the movable cylinder, and the outer blade is engaged with a spiral groove provided on an inner peripheral surface of the fixed cylinder. The helical blade type compressor according to any one of claims 9 to 14, wherein