KR100213403B1 - Fluid compressor - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor capable of balancing a crankshaft having a crank portion for pivoting a roller, wherein the cylinder (5) and the roller (by rotating the eccentric roller (11) arranged in the cylinder (5) 11) In the fluid compressor having the compression mechanism 3 for compressing the refrigerant gas introduced therebetween, the compression mechanism 3 is installed in the roller 11 and rotates the roller 11 in the cylinder 5. Two balance weights 9b provided with a crankshaft 9 having a crank portion 9a and fitted with a crank portion 9 in the axial direction of the crank shaft 9. , 10) is installed.

Description

Fluid compressor

The present invention relates to a compression mechanism for use in, for example, a refrigeration cycle apparatus and compresses compressed fluid such as refrigerant gas.

BACKGROUND ART Conventionally, a fluid compressor for compressing and discharging refrigerant gas introduced therein has been used for a refrigeration cycle apparatus or the like. One such fluid compressor is a helical blade type fluid compressor represented by Japanese Patent Application Laid-Open No. 7-107391.

Since the fluid compressor has a structure in which the cylinder and the roller rotate, the circumferential speed becomes large and it is necessary to consider the sliding motion loss in the bearing. For this reason, the fluid compressor shown in FIG. 3 is designed as a structure which reduces the circumferential speed and reduces the sliding motion loss.

In FIG. 3, "1" shows the closed case which made the axial direction horizontal. The compression mechanism part 3 and the electric motor part 4 are accommodated in this sealed case 1. That is, in FIG. 3, the right part becomes the compression mechanism part 3, and the left part becomes the electric motor part 4 in the axial direction of the substantially center part of the sealed case 1. As shown in FIG.

The said compression mechanism part 3 has the cylinder 5 which is a hollow cylinder which opened both ends. The main bearing 6 is attached and fixed to the side of the cylinder 5 on one side (left side of the drawing) through the fastener 7 so that the opening of the cylinder 5 is closed. On the side of the other direction side (right side of the drawing), the sub bearing 8 is attached and fixed through the fastener 7 so that the opening of the cylinder is closed.

The crankshaft 9 is inserted through the shaft center of the main bearing 6 and the sub bearing 8, and is rotatably supported. The crankshaft 9 not only penetrates into the cylinder 5 between the main bearing 6 and the sub bearing 8 but also protrudes from the main bearing 6 in the left direction of the drawing to be described later. The rotating shaft part 9Z of 4) is comprised. Further, the crank portion of the crank shaft 9 of the shaft center b which is eccentric with the shaft center a of the crankshaft by a predetermined dimension e on the circumferential surface between the main bearing 6 and the sub bearing 8 of the crankshaft 9. 9a) is integrally installed.

The roller 11 is sandwiched between the crankshaft 9 and the cylinder 5. This roller 11 is a cylindrical body with open ends, and its axial length coincides with the axial length of the cylinder 5.

The inner circumferential portion 12 of the roller 11 is formed in the inner circumferential portion 12 of the roller 11, and particularly in the portion facing the crank portion 9a of the crankshaft 9 in the same width as the crank portion, The inner hole support part 12a is rotatably slidably connected.

The outer circumferential surface of the roller 11 is provided with a helical groove 14 which gradually decreases in size from the end of the sub bearing 8 attachment side to the end of the main bearing 6 attachment side, and the helical groove 14 has a spiral shape. The blade 15 is wound around and mounted freely.

On the other hand, the motor unit 4 is the case body at a predetermined distance from the rotor 45 and the outer peripheral surface of the rotor 45 is fitted to the rotary shaft portion 9Z of the crankshaft 9 protruding from the main bearing (6) (1a) It is comprised by the stator 46 attached to the inner peripheral surface.

The fluid compressor configured as described above compresses the refrigerant gas as the compressed fluid as follows. That is, the crankshaft 9 is rotationally driven integrally with the rotor 45 by making the electric motor part 4 electrically. The rotational force of this crankshaft 9 is transmitted to the roller 11 through the crank part 9a.

The crank part 9a is provided eccentrically, and since the inner-hole support part 12a of the roller 11 hangs freely here, the roller 11 is pressed by the crank part 9a.

In addition, since the Oldham mechanism 13 interposed between the main bearing 6 and the roller 11 restricts the rotation of the roller, the roller 11 rotates without rotating.

On one side, a low pressure refrigerant gas is sucked from the suction pipe 17 and guided to the compression chamber 16. With the turning motion of the roller 11, the rotational connection position with respect to the inner peripheral surface of the cylinder 5 of a roller moves gradually in a circumferential direction, and the blade 15 enters and exits to the spiral groove 11. As shown in FIG. That is, the blade 15 moves in and out of the radial direction of the roller 11.

The refrigerant gas guided to the compression chamber 16 is sequentially transferred to the compression chamber 16 in accordance with the rotational movement of the roller 11 because the blade 15 is formed in a spiral shape.

The blade 15 is gradually set to a smaller pitch from the suction part A to the discharge part B side, and the refrigerant gas is compressed because the volume of the compression chamber 16 divided by the blade is reduced in turn. It is compressed during the transfer to the yarns one after another, and rises to a predetermined pressure in the compression chamber at the discharge part B side and becomes high pressure.

The high pressure gas is discharged from the compression chamber 16 of the discharge portion B and guided to the space portion on the side of the motor portion 4. And it leads to the space part by the side of the compression mechanism part 3, and fills it. Since the open end of the discharge tube 18 faces this space portion, the high pressure gas is led to the discharge tube and is led to the condenser.

Thus, since the fluid compressor rotates the roller 11 with respect to the cylinder 5 fixed to the compression mechanism part 3, the peripheral speed of the roller 11 becomes small compared with the conventional helical blade type compression mechanism. Therefore, the sliding loss in the thrust surface of the roller 11 can be reduced, and the compression efficiency is improved.

In the conventional fluid compression mechanism in which the roller 11 performs the pivoting motion as described above, there are the following problems. That is, since the crank portion 9a is formed on the crankshaft 9, it is necessary to solve the imbalance caused by the rotational movement of the roller 11 to reduce the vibration. The balance weight 9b was provided in the circumferential surface between bearing 8 support parts.

However, if there is only one balance weight, the balance is not balanced. Therefore, it is necessary to attach at least one to the main bearing and the sub bearing side of the crank portion 9a. However, when using the crankshaft (9) in which two balance weights are integrally installed, there is a problem that the balance waist cannot pass through the internal hole support part 12a and thus cannot be assembled. It is also conceivable to use a balance weight thinner than the internal hole support 12a, but there is a fear that the balance is not sufficiently balanced.

On the other hand, although two balance weights may be provided on the motor unit 4 side, there is a possibility that the crankshaft 9 bends in a high rotational region.

Accordingly, the present invention provides a fluid compressor for compressing a compressed fluid introduced between a cylinder and a roller by pivoting a roller disposed eccentrically in the cylinder, thereby balancing a crankshaft having a crank portion for pivoting the roller. It is an object of the present invention to provide a fluid compressor that can be easily assembled.

1 is a longitudinal sectional view showing a fluid compressor according to an embodiment of the present invention;

2 shows an essential part of the same apparatus;

3 is a longitudinal sectional view showing a conventional fluid compressor.

* Explanation of symbols for the main parts of the drawings

1: sealed case 3: compressor section

4: electric motor part 5: cylinder

6: main bearing 7: sub bearing

9: crankshaft 9a: crank part

9b, 10: Balance weight 11: Roller

12: Internal Studies 13: Oldham ’s Organization

14: spiral groove 15: blade

16: compression chamber

In order to solve the above problems and achieve the object, the invention described in claim 1 is a fluid having a compression mechanism for compressing a compressed fluid introduced between the cylinder and the roller by pivoting a roller disposed eccentrically in the cylinder. In the compressor, the compression mechanism is provided in the roller and has a crank shaft having a crank portion for pivoting the roller in the cylinder, wherein the crank shaft has two balances fitted with the crank portion in the axial direction thereof. Weight is installed.

In the invention according to claim 2, in the invention according to claim 1, the crankshaft is supported by the main bearing and the sub bearing, and the balance weight is disposed between the main bearing and the sub bearing.

In the invention according to claim 3, in the invention according to claim 1, one of the balance weights is integrally formed on the crankshaft, and the other balance weight is freely formed on the crankshaft.

In the invention according to claim 4, in the invention according to claim 3, relative movement of the other balance weight is controlled in the circumferential direction and the axial direction with respect to the crankshaft.

The invention according to claim 5 is the invention according to any one of claims 1 to 3, wherein the compression mechanism is provided along the circumferential surface of the roller and formed into a helical groove formed at a gradually smaller pitch, and the spiral groove. A spiral blade which freely fits and partitions the space with the cylinder into a plurality of compression chambers, the volume of which gradually decreases, and gradually spirals the compressed fluid sucked into the compression chamber on the side of which the pitch of the spiral groove is large. The pitch of the grooves is compressed while being transferred to the compression chamber on the smaller side.

As a result of providing the above means, the following actions occur. The invention according to claim 1 can be balanced because two balance weights are provided in which a crank part is fitted in an axial direction on a crank shaft having a crank part for pivoting a roller in a cylinder, thereby balancing the balance between weight and moment. It can be secured.

Since the balance weight is arrange | positioned between the main bearing and the subordinate bearing which support a crankshaft, invention of Claim 2 can prevent a crankshaft from bending, for example, when a balance weight is attached to the motor side.

In the invention according to claim 3, one of the balance weights is integrally formed on the crankshaft, and the other balance weight is formed by being fitted to the crankshaft, so that the other balance weight is attached after assembling the crankshaft to the roller. Can be. For this reason, when assembling a crankshaft to a roller, a crankshaft can be inserted easily, even if the internal diameter of a roller and a part which contact | connects a crank part is small, for example.

In the invention according to claim 4, the other balance weight can be balanced because relative movement is restricted in the circumferential direction and the axial direction with respect to the crankshaft.

In the invention according to claim 5, the compression mechanism is provided with a spiral groove formed along a circumferential surface of the roller to form a gradually smaller pitch, and a plurality of compression chambers that allow the entrance and exit of the spiral groove to freely enter the space. The compressed fluid suctioned into the compression chamber on the side of the spiral groove having a spiral blade to be partitioned was gradually compressed while transferring to the compression chamber on the side of the pitch of the spiral groove. For this reason, the helical blade type fluid compressor which has good assembly property can be provided.

Embodiment of the Invention

EMBODIMENT OF THE INVENTION Hereinafter, one Embodiment of this invention is described based on drawing, The helical blade type fluid compressor disclosed here shall be used for the refrigeration cycle of an air conditioner, for example. In addition, in this figure, the same code | symbol is attached | subjected to the same functional part as FIG.

As shown in FIG. 1, the sealed case 1 includes a case body 1a having both ends opened in an axial direction in a horizontal direction, an upper cover 1b for closing one opening of the case body 1a, and the other end opening. It consists of a closing cover plate 1c.

The compression mechanism part 3 and the electric motor part 4 are accommodated in this sealed case 1. That is, in FIG. 1, the right part becomes the compression mechanism part 3, and the left part becomes the electric motor part 4 in the axially nearly center part of the sealed case 1. As shown in FIG.

The said compression mechanism part 3 is a hollow cylinder which open | released the both ends, and has the cylinder 5 provided by the pair of the shading parts 5a5b protruding on the outer peripheral surface of this both end side. At least one sunshade 5a of the cylinder 5 is attached to the case body 1a constituting the sealed case 1 and is fixed to determine the position of the cylinder 5.

The main bearing 6 is attached and fixed to the side of one side (left side of the drawing) of the cylinder 5 via the fastener 7 so that the opening of the cylinder is closed. On the side of the other side (right side of the drawing), the sub bearing 8 is attached and fixed through the fastener 7 so that the opening of the cylinder is closed.

The crankshaft 9 is inserted along the shaft center of the main bearing 6 and the sub bearing 8, and is rotatably supported. The crankshaft 9 not only penetrates into the cylinder 5 between the main bearing 6 and the sub bearing 8, but also protrudes from the main bearing 6 in the left direction of the drawing to be described later. ) Constitutes a rotating shaft portion 9Z.

The crankshaft 9 will be described in an axial center spaced apart from each other on the circumferential surface between the main bearing 6 and the sub bearing 8 and by a predetermined pitch e with the crankshaft shaft center a. The crank portion 9a of (b) is integrally molded.

The balance weight 9b is provided integrally with the crankshaft further adjacent to the left portion of the crank portion 9a. The balance weight 9b is eccentrically formed on the circumferential surface portion on the side opposite to the direction in which the first crank portion 9a eccentrically protrudes.

In addition, the balance weight 10 is fitted and attached to the right side of the crank portion 9a separately from the crank shaft 9. This balance weight 10 is eccentric to the peripheral surface part on the opposite side to the eccentric protrusion direction of the crank part 9a. In addition, as shown to (a) and (b) of FIG. 2, the balance weight 10 is circumferentially with respect to the crankshaft 9 by the key 50 which fits in the key groove 9c provided in the crankshaft 9. As shown to FIG. Movement in the direction is regulated. In addition, the movement in the axial direction with respect to the crankshaft 9 is restricted by the stop ring 51. In addition, the procedure which attaches the balance weight 10 to the crankshaft 9 is attached later.

Between the crankshaft 9 and the cylinder 5, a roller 11 selected from a material of aluminum alloy, for example, whose specific gravity is smaller than that of iron is inserted. The roller 11 is a cylindrical body whose ends are open, and the length in the axial direction coincides with the axial length of the cylinder.

The inner circumferential portion 12 of the roller 11 is formed with a short inner hole 12, and particularly in a portion facing the crank portion 9a of the crankshaft 9 with the same width as the crank portion 9a, Moreover, the inner hole support part 12a which is rotatably connected to the inner peripheral surface is formed.

As a result, the shaft center b of the roller 11 coincides with the shaft center b of the crank portion 9a, and is eccentric with respect to the shaft center a of the cylinder 5 or the like by e size. A portion of the outer circumferential wall of the roller 11 is sized to rotate in a axial direction to a portion of the inner circumferential wall of the cylinder 5.

Further, the sliding connection portion between the crank portion 9a of the crankshaft 9 and the inner hole supporting portion 12a of the roller 11 is set at a position spaced equally to the left and right at the central portion of the roller 11 in the axial direction. have.

An Oldham mechanism 13 is fitted between the end portion of the main bearing 6 side of the roller 11 and the main bearing 6 portion. This Oldham mechanism 13 regulates the rotation of the roller 11.

For this reason, when the crankshaft 9 rotates, the crank part 9a provided here rotates eccentrically and the roller 11 supported by the inner peripheral surface of this crank part 9a eccentrically moves. Do it.

In addition, the rotational connection portion of the roller 11 outer circumferential wall with respect to the inner circumferential wall of the cylinder 5 moves gradually along the circumferential direction of the cylinder 5 as the roller 11 rotates.

The outer circumferential surface of the roller 11 is provided with a spiral groove 14 for gradually reducing the pitch from the end portion of the secondary bearing 8 attachment side to the end portion of the main bearing 6 attachment side, which is spirally formed. The upper blade 15 is wound up and mounted freely.

For example, the blade 15 may be formed of a highly active material such as fluorine resin, and its inner diameter may be larger than the outer diameter of the roller 11. That is, the blade 15 is fitted into the spiral groove 14 by forcibly reducing the diameter, so that the outer circumferential surface of the blade 15 is always in the state assembled in the cylinder 5 for each roller 11. The cylinder 5 is expanded and deformed to elastically contact the inner circumferential wall.

As described above, when the roller 11 pivots and the rotational connection position with respect to the cylinder 5 moves, the rotational connection portion approaches, and the blade 15 is immersed in the spiral groove 14 to be at the rotational connection position. The outer peripheral surface of the blade 15 is completely the same as the outer peripheral surface of the roller 5.

On the contrary, when the rotational connection part passes, the blade 15 protrudes from the spiral groove 14 according to the distance from here, and the blade 15 at the part facing 180 ° through the axis center b with the rotational connection part. Since the protruding length of is maximized, the above-described action is obtained since the approaching portion of the rotary connection is approached again.

When the cylinder 5 and the roller 11 are divided along the radial direction, the roller 11 is accommodated eccentrically with respect to the cylinder 5, and since a part of the circumferential surface of the roller is connected to the cylinder, A crescent shaped space portion is formed between the cylinder 5 and the roller 11.

When the space portion is viewed along the axial direction, the blade 15 is wound and mounted on the spiral groove 14 of the roller 11, and since the outer peripheral surface thereof is rotatably connected to the inner peripheral wall of the cylinder 5, the roller 11 and the cylinder are mounted. Between 5, it is divided by the blade 15 into several space part.

This divided space part is called the compression chamber 16. The volume of each compression chamber 16 gradually decreases from the end of the sub bearing 8 side to the end of the main bearing 6 side because of the setting of the helical groove 14.

On the other hand, a suction pipe 17 penetrates the cover plate 1c constituting the sealed case 1, and a discharge pipe 18 is connected to the vicinity thereof. The suction pipe 17 communicates with the evaporator constituting the refrigeration cycle, and the discharge pipe 18 communicates with the condenser constituting the refrigeration cycle. (Not shown all)

The suction pipe 17 which penetrates the said sealing case cover plate 1c is connected to the connection part 8a provided in the said sub bearing 8 in the inside of the sealing case 1. This connecting part 8a is open to the cylinder 5 joining surface of the sub bearing 8. The discharge tube 18 directs its open end into the sealed case 1.

The recessed part 19 is provided in the awning part 5b part of the cylinder 5 which opposes the opposing end of the said sub bearing connection part 8a, and is made to collect the gas introduce | transduced in the suction pipe 17 once.

At one end of the roller 11, a recess for a gas passage (not shown) is provided. This gas passage concave portion opposes the concave depression 19 provided in the cylinder 5 at any position in which the roller 11 which makes a pivotal movement.

Therefore, a buffer portion 21 having a large volume for storing gas introduced into the suction pipe 17 from the gas passage recess and recess 19 is formed.

A discharge hole 24 is provided in the side portion of the main bearing 6. The space portion at the end of the cylinder 5 and the roller 11 side and the space portion at the electric motor portion 4 side pass through this discharge hole 24.

Due to the setting of the pitch of the spiral groove 14, the compression chamber 16 on the side where the buffer portion 21 is installed becomes the suction portion A, and the side on which the discharge hole 24 on the opposite side is provided. Compression chamber 16 becomes discharge part B. FIG.

In addition, a first space portion 25 surrounded by the main bearing 6, the crankshaft 9, and the roller 11 is formed. A second space 26 surrounded by the secondary bearing 8, the crankshaft 9 and the roller 11 is formed.

The guide hole 28 is provided over the support part of the main bearing 6 which is the intermediate part of the cross section of the side of the said bearing 8 side of the said crankshaft 9, and along the axial center of a crankshaft.

The opening end of this guiding hole 28 and the shaft support part opening end of the sub bearing 8 are closed by the sealing plate 30 attached to the end bearing end face via the fixture 29.

The guide holes 28 and the outer circumferential surfaces of the crankshaft 9 are successively passed through a plurality of oil holes described later.

That is, the 1st oil hole 31 is provided in the site which communicates with the said 1st space part 25. As shown in FIG. The 2nd oil hole 32 is provided in the site which communicates with the said 2nd space part 26. As shown in FIG.

The third oil hole 33 is opened with respect to the support of the sub bearing 8. The fourth oil hole 34 opens to the circumferential surface of the crank portion 9a and faces the second inner wall support portion 12a of the roller 11. The fifth oil hole 35 is opened with respect to the support of the main bearing 6. An oil supply passage S composed of the third to fifth oil holes 33 to 35 is formed together with the guide hole 28.

An inner bottom portion of the sealed case 1 is formed with an oil reservoir 37 for collecting and storing lubricating oil.

The oil suction pipe 38 connected to the shaft support part of the sub bearing mechanism 8 is immersed in the lubricating oil of this oil storage part 37.

The connection part of this oil suction pipe 38 is connected to the sliding connection surface of the crankshaft 9 which is the inner peripheral surface of the sub bearing 8 support part. The oil supply pump part 39 is provided in the crankshaft part which opposes this.

In the shade 5a of the cylinder 5 press-fitted into the case body 1a, a gas guide hole 43 is provided in the upper side of the drawing, and in the portion immersed in the lubricating oil of the lower oil storage unit 37, An oil guide hole 44 is provided.

Each of the guide holes 43 and 44 penetrates both sides of the shade portion 5a, and passes through the inside of the sealed case 1 divided by the shade portion. That is, the gas guide hole 43 is for guiding through the high pressure gas discharged from the discharge part B, and the oil guide hole 44 is for guiding the lubricating oil of the oil storage part 37 to guide it. .

On the other hand, the electric motor portion 4 has a rotor 45 attached to the rotary shaft portion 9Z of the crankshaft 9 protruding from the main bearing 6 and a predetermined gap with the outer circumferential surface of the rotor 45. It consists of a stator 46 fitted to the inner peripheral surface of the case body (1a).

Therefore, the balance weight 10 is attached to the crankshaft 9 in the following order. In addition, the balance weights 9b and 10 are generally formed to have a larger diameter than the internal pore support portion 12a in order to ensure balance, so that the balance weights 9b and 10 form the internal pore support portion 12a of the roller 11. You cannot pass one after another. Therefore, the following procedure is required.

That is, the crankshaft 9 is inserted in the roller 11 from the right side in FIG. For this reason, the inner hole support part 12a of the roller 11 can oppose the crank part 9a without passing through the part of the balance weight 9b. On the other hand, after the balance weight 10 is attached to the right side of the crankshaft 9 from the right side in FIG. 1, the balance weight 10 does not pass through the inner hole supporting portion 12 of the roller 11 at a predetermined position. It can be attached to. Then, the balance weight 10 is fixed by the key 50 and the ring 51.

The helical braided fluid compressor thus constructed operates as follows. In other words, the crankshaft 9 is integrally rotated and driven together with the rotor 45 through the electric motor 4. The rotational force of this crankshaft 9 is transmitted to the roller 11 through the crank part 9a.

That is, the crank part 9a is provided eccentrically, and since the inner hole support part 12a of the roller 11 is rotatably engaged with it, the roller 11 is pressed by the crank part 9a. Moreover, since the Oldham mechanism 13 inserted between the main bearing 6 and the roller 11 restricts the rotation of the roller 11, the roller 11 does not rotate but rotates.

The refrigerant gas of low pressure is sucked in one side of the suction pipe 17, and is temporarily stored in the buffer part 21 formed with the cylinder 5 and the roller 11. As shown in FIG. And it leads to the compression chamber 16 by the suction part A side.

The rotational connection position with respect to the inner peripheral surface of the cylinder 5 of the roller 11 moves gradually in a circumferential direction according to the rotational motion of the roller 11, and the blade 15 enters and exits with respect to the helical groove 14. As shown in FIG. That is, the blade 15 moves in and out of the radial direction of the roller 11.

Since the blade 15 is formed in a spiral shape, the refrigerant gas guided to the compression chamber 16 on the suction part A side has a compression chamber 16 toward the discharge part B in accordance with the rotational movement of the roller 11. In turn.

The blade 15 is set in such a manner that the pitch decreases in order from the suction part A to the discharge part B side, and the volume of the compression chamber 16 divided by the blade 15 decreases in sequence, so that the refrigerant gas Is compressed during the transmission to the compression chamber in turn, and is increased to a predetermined pressure in the compression chamber closest to the discharge part B side to increase the pressure.

The high-pressure gas is discharged from the compression chamber 16 of the discharge part B, filled in the first space part 25, and then through the discharge hole 24 provided in the main bearing 6 to the electric motor part 4 side. Is led to the space department. Then, the gas guide hole 43 provided in the shade 5a of the cylinder 5 leads to the space portion on the compression mechanism 3 side and is filled.

Since the open end of the discharge tube 18 faces the space portion, the high pressure gas is led to the discharge tube 18, where it is led to the condenser.

In this way, in the present invention, the helical blade type compression mechanism 3 is provided with a balance weight 9b, at a position in which the crank portion 9a provided to pivot the roller 11 with respect to the fixed cylinder 5 in the axial direction. 10) can be balanced. In addition, since one balance weight 10 is formed to fit the crankshaft 9, the outer diameter of the balance weight 10 and the inner diameter of the inner hole support part 12a of the roller 12a are taken into consideration when assembling. There is no need. For this reason, even when the balance weight 10 is large, the assembly is possible, and the balance can be completed by the balance weights 9b and 10. Therefore, the vibration at the time of fluid compressor operation can be made very small.

On the other hand, since the balance weights 9b and 10 are all disposed between the main bearing 6 and the sub bearing 8, the crankshaft 9 is bent when the balance weight is arranged on the motor part 4 side. You can prevent it.

Since the balance weight 10 is controlled relative to the crankshaft 9 in the circumferential direction by the key 50, and the balance weight 10 is restricted in the axial direction by the ring 51, the balance weight 10 is controlled. ) Can be prevented from moving during the operation of the fluid compressor to maintain the balance.

In addition, this invention is not limited to said embodiment. That is, although the helical braided fluid compressor has been described in the above embodiment, it may be applied to a rotary fluid compressor. Instead of the balance weight 10, a balance weight in which the key is integrally formed may be used. It goes without saying that various modifications can be made without departing from the scope of the present invention.

According to the invention described in claim 1, the balance can be balanced, and the balance between the weight balance and the moment can be secured.

According to the invention described in claim 2, the crankshaft can be prevented from bending.

According to the invention of claim 3, when assembling the crankshaft to the roller, the inner diameter of, for example, a portion where the crank portion contacts the roller can be easily inserted into the crankshaft.

According to invention of Claim 4, even if rotation is started, balance can be maintained.

According to the invention of claim 5, it is possible to provide a helical blade-type fluid compressor having good assembly properties due to easy attachment of the balance weight.

Claims (5)

A fluid compressor comprising a compression mechanism for compressing a compressed fluid introduced between the cylinder and the roller by pivoting a roller disposed eccentrically in the cylinder. The compression mechanism has a crankshaft installed in the roller and having a crank portion for pivoting the roller in the cylinder, The crankshaft is provided with two balance weights fitted with the crank in the axial direction thereof. The method of claim 1, The crankshaft is supported by the main bearing and the secondary bearing, And the balance weight is arranged between the main bearing and the sub bearing. The method of claim 1, One of the balance weights is integrally formed with the crankshaft, and the other balance weight is formed by being fitted to the crankshaft. The method of claim 3, wherein And said other balance weight is controlled relative to the crankshaft in its circumferential direction and axial direction. The method according to any one of claims 1 to 3, The compression mechanism is provided along the circumferential surface of the roller and the spiral groove formed in a gradually smaller pitch, And a spiral blade which partitions the space with the cylinder into a plurality of compression chambers in which the volume is freely inserted into the spiral groove so that the volume gradually decreases. And compressing the compressed fluid sucked into the compression chamber on the side with the large pitch of the spiral groove while gradually transferring the compressed fluid to the compression chamber on the side with the small pitch of the spiral groove.

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