KR980009938A - 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 section with a crank section for pivoting a roller, wherein the cylinder (5) is pivoted by pivoting a roller (11) disposed eccentrically in the cylinder (5). And a crankshaft (9) installed in the roller (11) and having a crank portion (9a) for pivoting the roller (11) in the cylinder (5), in the axial direction of this crank shaft (crank shaft). Two balance weights 9b and 10 provided with the crank portion 9 fitted therein are provided.

Description

Fluid compressor

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

2 shows a main part of the same apparatus.

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

* Explanation of symbols for 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: crankshaft

9b, 10: balance weight 11: roller

12: Internal Studies 13: Oldham`s Organization

14: spiral groove 15: blade

16: compression chamber

Detailed description of the invention

[Technical Field to which the Invention belongs and Prior Art in the Field]

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 a refrigerant gas introduced therein has been used for a refrigeration cycle device 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 a sealed case with the axial direction in the horizontal direction. The compression mechanism part and the electric aspherical part are accommodated in this sealed case. That is, in FIG. 3, the right side portion is the compression mechanism portion and the left side portion is the electric motor portion, with the boundary almost in the axial direction of the sealed case.

The said compression mechanism part has the cylinder which is a hollow cylinder which opened both ends. On the side of the cylinder in one direction (left side of the drawing), the main bearing is attached and fixed through the fixture to close the opening of the cylinder. On the side of the other direction side (right side of the drawing), the secondary bearing is attached and fixed through the fixture to close the opening of the cylinder.

The crankshaft is inserted and supported freely along the axis of the main bearing and the overbearing bearing. The crankshaft 9 not only penetrates into the cylinder between the main bearing and the sub bearing, but also protrudes from the main bearing in the left direction of the drawing to constitute a rotating shaft portion 9Z of a power mechanism described later. Further, on the circumferential surface between the main bearing and the sub bearing of the crankshaft 9, the crank portion 9a of the shaft center b, which is eccentric with the shaft center a of the crankshaft 9 by a predetermined dimension e, is provided. It is installed integrally.

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

The inner circumferential portion of the roller is provided with a short inner hollow portion, and in particular, a portion facing the crank portion of the crankshaft 9 has the same width as the crank portion, and the inner circumferential support portion which is freely slidably connected to the outer circumferential surface. As it is.

The outer peripheral surface of the roller is provided with a spiral groove which gradually decreases in size from the secondary bearing attachment end to the main bearing attachment end, and the spiral horn is mounted freely and wound around the spiral horn.

On the other hand, the motor unit is composed of a rotor fitted to the rotating shaft portion of the crankshaft (9) protruding from the main bearing and a stator fitted to the inner circumferential surface of the case body at a predetermined distance from the outer peripheral surface of the rotor.

The fluid compressor configured in this way compresses the refrigerant gas as the compressed fluid as follows. In other words, the crankshaft 9 is integrally rotated together with the rotor by allowing the electric motor to be electrically driven. The rotational force of this crankshaft 9 is transmitted to the roller through the crank part.

The crank part is provided eccentrically, and the roller is pressed by the crank part because the inner hole supporting part of the roller is freely hung therein.

In addition, the Oldham mechanism inserted between the main bearing and the roller regulates the rotation of the roller, so the roller does not rotate and rotates.

On one side, a low pressure refrigerant gas is sucked from the suction pipe and led to the compression chamber. With rotation of the roller, the rotational connection position with respect to the inner circumferential surface of the roller gradually moves in the circumferential direction, and the blade enters and exits the spiral groove. In other words, the blade moves in and out of the radial direction of the roller.

The refrigerant gas guided to the compression chamber is sequentially transferred to the compression chamber according to the rotational movement of the roller because the blade is formed in a spiral shape.

The blade is set such that the pitch gradually decreases from the suction part to the discharge part, and since the volume of the compression chamber divided by the blade is reduced in turn, the refrigerant gas is compressed while being sequentially transferred to the compression chamber, and at the most discharge part side. The pressure is increased to a predetermined pressure in the compression chamber.

The high pressure gas is discharged from the compression chamber of the discharge portion and guided to the space portion on the side of the motor portion. And it leads to the space part of a compression mechanism side, and is filled. Since the open end of the discharge tube is opposed to this space portion, the high pressure gas is led to the discharge tube and is led to the condenser.

As such, the fluid compressor rotates the roller with respect to the cylinder fixed to the compression mechanism, so that the peripheral speed of the roller becomes smaller than that of the conventional helical blade type compression mechanism. Therefore, the sliding loss in the thrust surface of the roller can be reduced, and the compression efficiency can be improved.

[Technical problem to be achieved]

In the conventional fluid compression mechanism, in which the conventional roller performs a pivoting motion, there are the following problems. That is, since the crankshaft 9 is formed with a crank part, it is necessary to reduce the vibration by reducing the imbalance caused by the rotational movement of the roller. Therefore, a balance weight is applied to the circumferential surface between the main bearing support and the sub-bearing support. Installed.

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 part. However, when using the crankshaft 9 in which two balance weights are integrally installed, there is a problem in that the balance weight cannot pass through the internal hole support part and thus cannot be assembled. Also, a balance weight thinner than the internal hole support part is used. It is also thought that there is a possibility that it will not be balanced enough.

On the other hand, although two balance weights may be provided on the motor 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 a cylinder, wherein the crankshaft having a crank portion for pivoting the roller is balanced. It is an object of the present invention to provide a fluid compressor that can be easily assembled.

[Configuration and Function of Invention]

In order to solve the above problems and achieve the object, the invention described in claim 1 is a fluid compressor having a compression mechanism for compressing a compressed fluid introduced between the rollers by pivoting an eccentrically arranged roller in a cylinder. And the compression mechanism is provided in the roller and has a crankshaft having a crank portion for pivoting the roller in the cylinder, wherein the crankshaft is provided with two balance weights fitted with the crank portion in the axial direction thereof. It is.

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, the relative balance of the other balance weight is restricted relative to the crankshaft in the circumferential direction and the axial direction thereof.

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 a circumferential surface of the roller and is formed in a spiral groove formed at a pitch that gradually decreases, and freely enters and exits the spiral groove. The compressed fluid sucked into the plurality of compression chambers in which the space between the cylinders and the cylinders is gradually reduced is compressed while gradually transporting the compressed fluid to the compression chamber on the side with a small pitch of the spiral groove.

As a result of the provision of the above means, the following hospital use results. 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 rotating the roller in a cylinder, thereby balancing the balance between weight balance and moment. It can be secured.

According to the invention of claim 2, since the balance weight is disposed between the main bearing and the sub bearing supporting the crankshaft, the crankshaft can be prevented from bending, for example, when the balance weight is attached to the motor side.

In the invention according to claim 3, one of the balance weights is integrally molded to the crankshaft, and the other balance weight is formed by being fitted to the crankshaft. Can be. For this reason, when assembling a crankshaft to a roller, a crankshaft can be easily inserted even if the internal diameter of a part which contact | connects a roller and 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 compressed while being fed along the circumferential surface of the roller to form a spiral groove formed in a gradually decreasing pitch and a compression chamber on the side where the pitch of the spiral groove is small. This makes it possible to provide a assembleable helical bladed fluid compressor.

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 is composed of an upper cover which closes one end opening of the case body whose both ends are opened in the axial direction in the horizontal direction and a cover plate which closes the other end opening.

The compression mechanism part and the electric motor part are accommodated in this sealed case. That is, in FIG. 1, the right side portion is the compression mechanism portion and the left side portion is the electric motor portion in the axially near center portion of the sealed case.

The said compression mechanism part is a hollow cylinder which opened both ends, and has the cylinder provided with the pair of shading parts protruding on the outer peripheral surface of this both end side. At least one shading portion of the cylinder is fitted to the case body constituting the sealed case and fixed to determine the position of the cylinder.

On the side of one side of the cylinder (left side of the drawing), the main bearing is attached and fixed through the fixture to close the opening of the cylinder. On the side of the other side (right side of the drawing), the sub-bearings are attached and fixed through the fasteners to close the opening of the cylinder.

The crankshaft is inserted and supported freely along the axis of the main bearing and the sub bearing. The crankshaft not only penetrates into the cylinder between the main bearing and the sub-bearing, but also protrudes from the main bearing in the left direction of the drawing to constitute a rotating shaft of the electric motor described later.

In the description of the crankshaft, a crank portion of an axial core which is eccentric with a predetermined pitch at a position separated from each other and with respect to the crankshaft axial center is integrally formed on the circumferential surface between the main bearing and the sub bearing.

A balance weight is provided integrally with the crankshaft further adjacent to the left side of the crank portion. The balance weight is eccentrically through an axial center on the circumferential surface portion opposite to the direction in which the first crank portion eccentrically protrudes.

In addition, a balance weight is fitted and attached adjacent to the right side of the crank part separately from the crankshaft. This balance weight is eccentric to the peripheral surface portion on the side opposite to the eccentric protrusion direction of the crank part. In addition, as shown in (a) and (b) of FIG. 2, the balance weight is controlled to move in the circumferential direction with respect to the crankshaft by a key fitted to a key groove provided in the crankshaft. In addition, the movement in the axial direction with respect to the crankshaft is restricted by the stop ring. In addition, the procedure which attaches a balance weight to a crankshaft is mentioned later.

Between such a crankshaft and the cylinder, a roller having a specific gravity smaller than that of iron, for example, made of a material of an aluminum alloy is inserted. This is a cylindrical body which is open at both ends, and its axial length coincides with the axial length of the cylinder.

The inner circumferential portion of the roller is formed with a short inner hollow portion, and in particular, a portion facing the crank portion of the crankshaft is formed with an inner hollow support portion having the same width as the crank portion and rotatably connected to the inner circumferential surface.

As a result, the shaft center of the roller coincides with the shaft center of the crank part, and is eccentrically by e size with respect to the shaft center of the cylinder or the like. In addition, a part of the outer circumferential wall of the roller is sized to rotate in a axial direction to a part of the inner circumferential wall of the cylinder.

Further, the sliding connection portion between the crank portion of the crankshaft and the inner hole supporting portion of the roller is set at a position spaced equally from the center in the axial direction of the roller.

The Oldham mechanism is fitted between the main bearing side end of the roller and the main bearing portion. This Oldham organization regulates the rotation of rollers.

For this reason, when the crankshaft rotates, the crank portion provided here is eccentrically rotated, and the roller supported by the inner circumferential surface of the crank portion is eccentrically moved.

In addition, the rotational connection portion of the roller outer circumference with respect to the inner cylinder wall of the roller is gradually moved along the circumferential direction of the cylinder as the roller moves.

The outer circumferential surface of the roller is provided with a spiral groove which gradually reduces the pitch from the sub bearing attachment side end to the main bearing attachment side end, and the spiral groove is freely wound around the spiral groove.

For example, the blade may be made of a highly active material such as fluorine resin, and its inner diameter may be larger than that of the roller. That is, the blade is closely fitted to the spiral groove in the state of forcibly reduced diameter, and as a result, the outer peripheral surface of the blade is expanded and deformed so as to elastically contact the inner circumferential wall of the cylinder in the state of being assembled in the cylinder for each roller.

As described above, when the roller rotates and the rotational connection position with respect to the cylinder moves, the rotational connection portion approaches, and the blade is immersed in the spiral groove so that the blade outer circumferential surface is exactly the same as the roller outer circumferential surface at the rotational connection position.

On the contrary, when the rotary connection part passes, the blade protrudes from the spiral groove according to the distance from here, and the blade length of the blade is maximized at the part facing 180 ° through the axis from the rotary connection part. After this, the above-described action is obtained because the rotating connection part approaches again.

When the cylinder and the roller are divided along the radial direction, the roller is eccentrically received with respect to the cylinder, and a part of the circumferential surface of the roller is connected to the cylinder so that a crescent-shaped space is formed between the cylinder and the roller. do.

The blade is wound around the helical groove of the roller to be mounted along the axial direction. Since the outer circumferential surface thereof is rotatably connected to the inner wall of the cylinder, the blade is divided into a plurality of spaces by the blade between the roller and the cylinder.

This divided space is called a compression chamber. The volume of each compression chamber gradually decreases from the sub bearing side end to the main bearing side end because of the formation of the bare grooves.

On the other hand, the cover plate which comprises the said sealing case is provided with the suction pipe penetrating, and the discharge pipe is connected to this near-end position. The suction pipe communicates in series with the evaporator constituting the refrigeration cycle, and the discharge tube communicates with the condenser constituting the refrigeration cycle in a similar manner (both not shown).

The suction pipe which penetrates the said sealing case cover plate is connected to the connection part provided in the said sub bearing inside the sealing case. This connection is opened to the cylinder joint surface of the sub bearing. The discharge tube directs its open end into the sealed case.

A recessed portion is provided in the shade portion of the cylinder opposite to the opposite end of the sub-bearing connecting portion to collect the gas introduced from the suction pipe once.

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

Therefore, a buffer portion having a large volume for storing gas introduced into the suction pipe in the gas passage recess and recess portion once is formed.

A discharge hole is provided in the side portion of the main bearing. Through this discharge hole, the space portion at the end of the cylinder and roller side and the space portion at the motor side are successively passed through.

Due to the setting of the pitch of the spiral grooves, the compression chamber on the side where the buffer part is provided becomes the suction part, and the compression chamber on the side where the discharge hole on the opposite side is provided becomes the discharge part.

A first space portion surrounded by the main bearing, the crankshaft, and the roller is formed. A second space portion formed by the sub-bearing, the crankshaft and the roller is formed.

A guide hole is provided over the supporting portion of the main bearing, which is the intermediate portion of the sub-bearing side end face of the crankshaft, and along the axis of the crankshaft.

The opening end of this guiding hole and the shaft support part opening end of the sub-bearing are closed by a sealing plate attached to the sub-bearing end face through a fixture.

The opening end of the guiding hole 샤프트 the shaft support part opening end of the sub-bearing is closed by a sealing plate attached to the sub-bearing end face through a fixture.

The guide hole and the crankshaft outer circumferential surface are successively passed through a plurality of oil holes described later.

That is, the hole for 1st oil is provided in the site which communicates with the said 1st space part. The 2nd oil hole is provided in the site which communicates with the said 2nd space part.

The third oil hole is opened with respect to the support of the sub bearing. The fourth oil hole is opened to the circumferential surface of the crank portion to face the second inner wall support portion of the roller. The fifth oil hole is opened to the support of the main bearing. An oil supply passage S composed of the third to fifth oil holes is formed together with the guiding holes.

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

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

The connection part of this oil suction pipe is connected to the sliding connection surface of the crankshaft which is an inner peripheral surface of a sub bearing support part. On the opposite crankshaft section, an oil supply pump section is provided.

A gas guide hole is installed at the upper side of the drawing, and an oil guide hole is installed at a part immersed in the lubricating oil of the lower oil storage part.

Each guide hole penetrates both sides of the sunshade, and passes through the inside of the sealed case divided by the sunshade. That is, the gas guide hole is for guiding through the high pressure gas discharged from the discharge portion, and the oil guide hole is for guiding the lubricating oil through the oil storage portion.

On the other hand, the motor unit is composed of a rotor fitted to the rotating shaft portion of the crankshaft protruding from the main bearing and a stator fitted to the inner circumferential surface of the case body with a predetermined gap with the outer peripheral surface of the rotor.

Therefore, the balance weight is attached to the crankshaft in the following order. In addition, the balance weight is usually formed to have a larger diameter than the internal pore support portion in order to ensure balance, so that the balance weight cannot continuously notify the internal pore support portion of the roller. Therefore, the following procedure is required.

That is, the crankshaft is inserted into the roller from the right side in FIG. Because of this, the inner hole supporting portion of the roller can be opposed to the crank portion without passing through the portion of the balance weight. Meanwhile, the balance weight may be attached to a predetermined position without passing through the inner hole supporting portion of the roller by fitting the balance weight on the right side of FIG. 1 of the crankshaft. Then, the balance weight is fixed by the key and the ring.

The helical braided fluid compressor thus constructed operates as follows. That is, the crankshaft is integrally rotated and driven together with the rotor through the electric motor. The rotational force of this crankshaft is transmitted to the roller through the crank part.

That is, the crank part is provided eccentrically, and the roller is pressed by the crank part because the inner hole supporting part of the roller is fitted to rotate freely. In addition, since the Oldham mechanism inserted between the main bearing and the roller regulates the rotation of the roller, the roller does not rotate but rotates.

Low pressure refrigerant gas is sucked from one side of the suction pipe and temporarily stored in the buffer unit formed by the cylinder and the roller. And it leads to the compression chamber by the suction part side.

In accordance with the rotation of the roller, the rotational connection position with respect to the inner circumferential surface of the roller gradually moves in the circumferential direction, and the blade enters and exits from the spiral groove. That is, the blades move in and out in the radial direction of the roller.

The refrigerant gas guided to the compression chamber on the suction side is sequentially transferred to the compression chamber in the discharge direction in accordance with the rotational motion of the roller because the blades are formed in a spiral shape.

The blades are set in such a manner that the pitch decreases in order from the suction part to the discharge part side, and since the volume of the compression chamber divided by the blades is reduced in turn, the refrigerant gas is compressed while being sequentially transmitted to the compression chamber, and closest to the discharge part side. The pressure is increased to a predetermined pressure in the compression chamber.

The high pressure gas is discharged from the compression chamber of the discharge portion and filled to the first space portion, and then led to the space portion on the side of the motor portion through the discharge hole provided in the main bearing. Then, the gas is guided to the space portion on the compression mechanism side through the gas guiding hole provided in the shade portion of the cylinder to fill it.

Since the open end of the discharge tube is opposed to this space portion, the high pressure gas is led to the discharge tube, and is led to the condenser.

As described above, in the present invention, the helical blade type compression mechanism can be balanced because the balance weight is disposed at the position in which the crank part is installed in the axial direction so as to pivot the roller with respect to the fixed cylinder. In addition, since the Han Chinese balance weight is formed to fit the crankshaft, it is not necessary to take into account the outer diameter of the malle weight and the inner diameter of the inner hole supporting portion of the roller during assembly. Even if the balance weight is large on this gate, it can be assembled and the balance can be completed by the balance weight. Therefore, the vibration in the fluid compressor operation can be made very small.

On the other hand, since the balance weights are all disposed between the main bearing and the sub-bearings, it is possible to prevent the crankshaft from bending when the balance weight is arranged on the motor side. Since the balance weight is controlled relative to the crankshaft in the circumferential direction by the key 50, and the movement in the axial direction is regulated by the ring 51, the balance weight 10 is operated when the fluid compressor operates. It can be prevented from moving 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, a balance weight in which the key is integrally formed may be used. Of course, various modifications can be made without departing from the scope of the present invention.

[Effects of the Invention]

According to the invention described in claim 1, the balance can be achieved, 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 as set forth in claim 3, when assembling the crankshaft to the roller, the inner diameter of, for example, a portion where the crank portion is in contact with the roller can be more easily inserted into the crankshaft.

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

According to the invention as set forth in claim 5, it is possible to provide a helical blade type fluid compressor of which the balance weight is easily attached and which is easily assembled.

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, wherein the compression mechanism is installed in the roller and the roller is mounted on the roller. And a crankshaft having a crank portion for pivoting in the cylinder, wherein the crankshaft is provided with two balance weights fitted with the crank portion in the axial direction thereof. The fluid compressor of claim 1, wherein 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. The fluid compressor of claim 1, wherein one of the balance weights is integrally formed with the crankshaft, and the other balance weight is formed by being fitted to the crankshaft. 4. The fluid compressor according to claim 3, wherein the other balance weight is controlled relative to the crankshaft in the circumferential direction and the axial direction thereof. According to any one of claims 1 to 3, wherein the compression mechanism is provided along the circumferential surface of the roller spiral groove formed in a gradually smaller pitch, the spiral groove is freely inserted into the spiral groove and the cylinder and satin The spiral blade which partitions into the several compression chamber whose volume becomes small gradually, and the said compressed fluid sucked into the said compression chamber of the side where the pitch of the said spiral groove is large, the side where the pitch of the said spiral groove is small Compressing while conveying to the compression chamber of the fluid compressor. ※ Note: The disclosure is based on the original application.