JP2014214691A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas compressor capable of preventing or suppressing heat from degrading a lip seal interposed between a rotational shaft and a housing.SOLUTION: A gas compressor comprises: a compressor main body 60 having a compression chamber 48 compressing refrigerant gas G (gas) and a rotational shaft 51; and a housing 10 covering the compressor main body 60, including an intake chamber 13 that is formed therein and into which the refrigerant gas G supplied via an intake port (intake) is introduced, and including a lip seal (52) (seal member) arranged therein for sealing the intake chamber 13 from an outer circumferential surface 51a of the rotational shaft 51a. An intake hole 22 communicating the intake chamber 13 with the compression chamber 48 is formed in a front side block 20 (partition wall) isolating the compression chamber 48 from the intake chamber 13. A partitioned path 12j (path) is formed in the intake chamber 13 for causing the refrigerant gas G to reach the intake hole 22 via the seal chamber 13a (portion in which the lip seal (52) is arranged).

Description

  The present invention relates to a gas compressor, and in particular, to an improvement in a passage for a gas supplied to a compression chamber.

  Conventionally, a gas compressor (compressor) having a compression chamber that compresses a supplied gas such as a refrigerant gas into a high-pressure compressed gas is used in an air conditioning system (hereinafter referred to as an air conditioning system).

Here, the gas compressor includes a compressor main body having a compression chamber inside the housing, and a rotating shaft extending from the compressor main body passes through the housing because it is connected to a power source outside the housing.
A portion of the rotating shaft that penetrates the housing is provided with a rotating shaft seal for airtightly separating the inside and the outside of the housing (Patent Document 1).
Lubricating oil inside the gas compressor is supplied to the rotary shaft seal.

JP 2004-353620 A

Since the rotary shaft seal described above is in contact with the rotary shaft, frictional heat is generated by the rotation of the rotary shaft, and there is a possibility that performance such as durability of the rotary shaft seal may be reduced by this heat.
The present invention has been made in view of the above circumstances, and is a gas compression capable of preventing or suppressing the performance of a seal member such as a rotary shaft seal interposed between a rotary shaft and a housing from being deteriorated by heat. The purpose is to provide a machine.

In the gas compressor according to the present invention, a partitioned flow path is formed in the suction chamber to reach the suction hole leading to the compression chamber through the portion (seal chamber) where the seal member is disposed (seal chamber). The gas supplied to the suction chamber and introduced into the compression chamber is cooled by forcibly contacting the seal member of the seal chamber.
That is, the gas compressor according to the present invention covers a compressor body having a compression chamber and a rotating shaft for compressing supplied gas into a high-pressure compressed gas, the compressor body, and is supplied from the outside through a suction port. And a housing in which a sealing member for sealing a space between the suction chamber and the outer peripheral surface of the rotary shaft is disposed. The compression chamber, the suction chamber, A partition hole is formed with a suction hole through which the suction chamber and the compression chamber are passed, and the partition allows the gas to reach the suction hole through a portion where the seal member is disposed. The formed flow path is formed.

  The gas compressor according to the present invention can prevent or suppress the performance of the seal member interposed between the rotating shaft and the housing from being deteriorated by heat.

It is a disassembled perspective view which shows the vane rotary type compressor which is one Embodiment of the gas compressor which concerns on this invention. It is sectional drawing which shows the cross section in the surface orthogonal to the rotating shaft of the compressor shown in FIG. It is a fragmentary sectional view which shows the suction chamber formed between the front head and the front side block. It is the disassembled perspective view which displayed the front head and the front side block facing each other (illustration of the lip seal is omitted). It is a figure which shows the state which saw through the suction chamber from the outer surface side of the front head. It is a figure which shows the example using the separate duct as a channel | path.

  Hereinafter, an embodiment according to the gas compressor of the present invention will be described with reference to the drawings.

As shown in FIG. 1, a vane rotary compressor 100 (hereinafter simply referred to as a compressor 100), which is an embodiment of a gas compressor according to the present invention, houses a compressor body 60 inside a housing 10. .
The compressor 100 is configured as a part of an air conditioning system (hereinafter, simply referred to as an air conditioning system) that performs cooling using the heat of vaporization of a cooling medium, and includes a condenser and an expansion that are other components of the air conditioning system. Along with a valve, an evaporator, etc., it is provided on the circulation path of the cooling medium.

The compressor 100 compresses the refrigerant gas G (gas) as a gaseous cooling medium taken from the evaporator of the air conditioning system, and supplies the compressed refrigerant gas G to the condenser of the air conditioning system.
The condenser heat-exchanges the compressed refrigerant gas G with ambient air and the like to dissipate heat from the refrigerant gas G and liquefy it, and sends it to the expansion valve as a high-pressure liquid refrigerant.
The high-pressure liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from ambient air and vaporizes in the evaporator, and cools the air around the evaporator by heat exchange accompanying the vaporization of the refrigerant.
The vaporized low-pressure refrigerant gas G returns to the compressor 100 and is compressed, and the above steps are repeated thereafter.

The housing 10 includes a case 11 having one end closed and the other end open, and a front head 12 covering the other open end of the case 11. The front head 12 is attached to the case 11 by a fastening member 18 such as a bolt. It is assembled to.
With the front head 12 assembled to the case 11, a space is formed inside the housing 10, and the compressor body 60 is accommodated in the space.
The front head 12 is formed with a suction port 12a (suction port) for taking in the low-pressure refrigerant gas G supplied from the evaporator, and the case 11 has a high-pressure refrigerant compressed by the compressor body 60. A discharge port 11a for discharging the gas G to the condenser is formed.

  As shown in FIG. 2, the compressor main body 60 includes a rotary shaft 51 that is driven to rotate about the axis C, a columnar rotor 50 that rotates integrally with the rotary shaft 51, and an outer peripheral surface of the rotor 50. Is embedded in the outer periphery of the rotor 40 and the outer periphery of the rotor 50 so that the outer end of the cylinder 40 can protrude outwardly. The amount of protrusion is variable so as to follow the contour shape of the inner peripheral surface 49, and a plurality of sheets embedded in the rotor 50 at equiangular intervals around the rotation shaft 51 (the one shown is three, A plate-like vane 58 (which may be four or the like), a front side block 20 and a rear side block 30 fixed so as to cover the open end surfaces from the outside of the open end surfaces on both sides of the cylinder 40, and the rear side block 30. Ri attached, and includes an oil separator for separating refrigeration oil from the refrigerant gas G and a (not shown).

  And the volume of the three compression chambers 48 which are the space defined by the two side blocks 20 and 30, the rotor 50, the cylinder 40, and the two vanes 58 and 58 that follow each other along the rotation direction of the rotation shaft 51 is obtained. By repeating the increase / decrease according to the rotation of the rotary shaft 51, the refrigerant gas G is sucked into each compression chamber 48 (intake stroke), the refrigerant gas G is compressed within each compression chamber 48 (compression stroke), The process of discharging (discharge process) high-pressure refrigerant gas G from the compression chamber 48 is repeated.

The compressor 100 is configured to perform a series of cycles of a suction stroke, a compression stroke, and a discharge stroke twice while the rotary shaft 51 rotates once.
Accordingly, the two suction strokes, the two compression strokes, and the two discharge strokes are set in ranges that are shifted from each other by a rotation angle of 180 degrees.

  Inside the housing 10, a suction chamber 13, which is a space into which the refrigerant gas G supplied through the suction port 12a is introduced, is formed by the front head 12 and the compressor body 60, and the refrigerant gas passes through the discharge port 11a. A discharge chamber 14 that is a space through which G is discharged to the outside is formed by the case 11 and the compressor body 60.

As shown in FIG. 3, the suction chamber 13 is a space surrounded by the front head 12 and the front side block 20 (partition wall) of the compressor main body 60. Of the inner surface of the front head 12 shown in FIG. A portion 12b shaded with fine dots is in contact with the outer surface 20a of the opposed front side block 20, and an inner region surrounded by this contacting portion (shaded portion 12b) is formed as the suction chamber 13.
The suction chamber 13 and the compression chamber 48 are separated from each other by the front side block 20, but the two suction chambers that allow the suction chamber 13 and the two compression chambers 48 in the suction stroke to communicate with each other separately. Holes 22 and 23 are formed.
The two suction holes 22 and 23 are formed with a rotation angle of 180 [degrees] apart from each other around the rotation shaft 51, and one suction hole 22 is in a vertical direction (shown in FIGS. 2 to 4) than the other suction hole 23. (In the up and down direction in the state).

The front side block 20 is formed with a through hole 12m through which the rotating shaft 51 protruding from the compressor body 60 is exposed to the outside of the housing.
Here, since the outside of the housing 10 is at atmospheric pressure and the suction chamber 13 is at a pressure lower than atmospheric pressure, in order to seal the suction chamber 13 inside the housing 10 and the outside of the housing, A seal chamber 13a in which a lip seal 52 (seal member) is disposed is formed near the through hole 12m.

The seal chamber 13a is a columnar space surrounded by a cylindrical peripheral wall 12c centering on the through hole 12m. The cylindrical peripheral wall 12c rotates from the end surface of the front head 12 toward the front side block 20. It is formed by a rib extending substantially parallel to the shaft 51.
The lip seal 52 disposed in the seal chamber 13a is fixed to the inner surface of the peripheral wall 12c, and the lip of the inner peripheral portion is in contact with the outer peripheral surface 51a of the rotating rotary shaft 51, so There is an airtight separation.

The inner peripheral surface 12d of the front end portion of the peripheral wall 12c of the seal chamber 13a is loosely fitted with the outer peripheral surface 24 of the bearing of the front side block 20, and the seal chamber 13a is partitioned inside the suction chamber 13. Cutouts 12e and 12f are formed in the upper part of 12c and the part facing the lower suction hole 22, respectively.
The upper notch 12 e allows the seal chamber 13 a to communicate with the suction chamber 13.

Two partition ribs extending from the end face of the front head 12 toward the front side block 20 so as to surround the lower suction hole 22 from both ends of the peripheral wall 12c adjacent to the lower notch 12f. 12g and 12h are formed.
These partition ribs 12g and 12h are formed at the same height as the shaded portion 12b (FIG. 4) and abut against the outer surface 20a of the front side block 20.
As a result, the two partition ribs 12g and 12h together with the end surface of the front head 12 and the outer surface 20a of the front side block 20 form a passage 12j (flow passage) that directly connects the seal chamber 13a and the lower suction hole 22. doing.
The passage 12j is partitioned inside the suction chamber 13 by two partition ribs 12g and 12h, an end surface of the front head 12, and an outer surface 20a of the front side block 20.

According to the compressor 100 of the present embodiment configured as described above, the refrigerant gas G is supplied from the suction port 12a to the suction chamber 13 in the housing 10 as shown in FIGS.
The refrigerant gas G sucked into the suction chamber 13 is sucked into the compression chamber 48 of the compressor main body 60 through the upper and lower suction holes 22 and 23, respectively.

Here, since the passage 12j leading to the lower suction hole 22 is partitioned inside the suction chamber 13 by the peripheral wall 12c of the seal chamber 13a and the partition ribs 12g and 12h, the refrigerant gas sucked into the suction chamber 13 is obtained. The refrigerant gas G sucked into the compression chamber 48 from the lower suction hole 22 in G always passes through the seal chamber 13a surrounded by the peripheral wall 12c through the upper notch 12e of the peripheral wall 12c partitioning the seal chamber 13a. It passes through the passage 12j partitioned by the partition ribs 12g and 12h through the lower notch 12f.
That is, the refrigerant gas G flowing toward the suction hole 22 is always forcibly brought into contact with the lip seal 52 installed in the seal chamber 13a.

Since the inner peripheral portion of the lip seal 52 is in contact with the outer peripheral surface 51 a of the rotating shaft 51, frictional heat is generated with the rotation of the rotating shaft 51, but the flowing refrigerant gas G is always in contact with the lip seal 52. The generated heat is cooled.
Therefore, it is possible to prevent or suppress the performance of the lip seal 52 from being deteriorated by heat.
As a result, it is possible to prevent or suppress the leakage of the refrigerant gas G due to the deterioration of the performance of the lip seal 52 and the leakage of the refrigerating machine oil circulating in the housing 10 or the air conditioning system.

Further, when a vehicle or the like equipped with the air conditioning system including the compressor 100 is exposed to a cold state for a long time, the refrigerant gas G is liquefied, and the liquefied refrigerant (hereinafter referred to as liquid refrigerant) is sucked. May accumulate in the lower part of the chamber 13.
The compressor 100 is formed with two suction holes 22 and 23 communicating with the suction chamber 13, and the lower suction hole 22 is formed at a position lower than the upper suction hole 23. If the liquid refrigerant accumulates in the lower portion of the suction chamber 13, the liquid level of the liquid refrigerant may be higher than the suction hole 22 at a relatively low position.

Here, in the case of the conventional gas compressor, when the liquid refrigerant level is higher than the suction hole 22, the liquid refrigerant flows into the compression chamber 48 in the suction stroke through the suction hole 22, and the liquid refrigerant flows. The compression chamber 48 causes liquid compression in the compression stroke.
On the other hand, in the compressor 100 of the present embodiment, the suction hole 22 is partitioned inside the suction chamber 13 by the partition ribs 12g and 12h, the end surface of the front head 12 and the outer surface 20a of the front side block 20. Even when the liquid refrigerant level is high in the suction chamber 13, the liquid refrigerant is blocked by the partition ribs 12 g and 12 h, the end face of the front head 12 and the outer surface 20 a of the front side block 20. There is no inflow.

The end of the passage 12j on the side higher than the suction hole 22 opens into the seal chamber 13a through the notch 12f. The seal chamber 13a is also separated from the suction chamber 13 by the peripheral wall 12c. The upper wall of the peripheral wall 12c communicates with the suction chamber 13 in the portion where the notch 12e is formed.
Therefore, even if liquid refrigerant accumulates in the suction chamber 13, the liquid refrigerant does not flow into the suction hole 22 until the liquid refrigerant reaches the position of the notch 13 e, and the compression chamber 48. Liquid compression can be prevented or suppressed.

  The compressor 100 of the present embodiment is a part of the peripheral wall of the passage 12j formed by the partition ribs 12g and 12h formed on the front head 12, but the gas compressor according to the present invention is the same as that of this embodiment. The flow path (passage 12j in the compressor 100) that reaches the suction hole (suction hole 22 in the compressor 100) through the portion where the seal member is disposed (the seal chamber 13a in the compressor 100) is not limited. You may form by the partition rib extended toward the front head 12 from the main body 60 (for example, the front side block 20).

Further, the passage 12j may be formed by a tubular (for example, snorkel-shaped) duct separate from the front head 12 and the front side block 20.
For example, as shown in FIG. 6, a duct 80 in which a passage 83 is formed between an opening 81 and an opening 82 is used, and one opening 81 of the duct 80 is opposed to the suction hole 22 so as to face the front side block 20. By connecting and connecting the other opening 82 to the peripheral wall 12c so as to oppose the notch 12f of the peripheral wall 12c of the seal chamber 13a, a passage 83 that reaches the suction hole 22 through the seal chamber 13a may be formed. .
Also by the passage 83 formed in this way, the same operation and effect as the compressor 100 of the above-described embodiment can be obtained.

DESCRIPTION OF SYMBOLS 10 Housing 12 Front head 12a Suction port 12g, 12h Rib 12j Passage 13 Suction chamber 13a Seal chamber 14 Discharge chamber 20 Front side block 20a Outer surface 22, 23 Suction hole 51 Rotating shaft 51a Outer surface 52 Lip seal (seal member)
60 Compressor body 100 Vane rotary compressor (gas compressor)
G Refrigerant gas (gas)

Claims (4)

A compressor body having a compression chamber and a rotating shaft for compressing the supplied gas into a high-pressure compressed gas, and a suction chamber for accommodating the compressor body inside and introducing gas supplied from the outside through a suction port And a housing in which a seal member that seals between the outer peripheral surface of the rotary shaft in the suction chamber is disposed,
A suction hole that allows the suction chamber and the compression chamber to pass through is formed in a partition wall that separates the compression chamber and the suction chamber.
A gas compressor characterized in that a partitioned flow path for allowing the gas to reach the suction hole through a portion where the seal member is disposed is formed in the suction chamber.   2. The gas compressor according to claim 1, wherein the flow path is formed at a position where the gas inlet side is higher than the outlet side.   The gas compressor according to claim 1, wherein the flow path is formed by a rib extending from the inner surface of the housing toward the partition and the partition.   The flow path is formed by a duct formed in a cylindrical shape with one end opening connected to a portion where the seal member is disposed and the other end opening connected to a front suction hole. The gas compressor according to claim 1 or 2.