JP2004308460A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce a manufacturing cost by dispensing with an O ring mounted to a rear side block. <P>SOLUTION: A cylinder 104 is formed with a delivery hole 16, and a compression chamber 14 and a delivery valve chamber 145 are made to communicate with each other. The delivery valve chamber 145 is formed between an inner peripheral surface and an outer peripheral surface of the cylinder 104, and is surrounded by a cylinder passage hole 143 formed to pass through along the axial direction of the cylinder 104, a front side block 2, and the rear side block 103. Accordingly, the delivery valve chamber 145 prevents refrigerant gas from leaking from the cylinder passage hole 143 to a gap 104a between a case 152 and the cylinder 104. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a gas compressor, and more particularly, to a gas compressor that can reduce manufacturing costs by eliminating an O-ring attached to a rear side block.
[0002]
[Prior art]
BACKGROUND ART Conventionally, a gas compressor as exemplified in Patent Literature 1 has been known as a device for compressing a refrigerant gas in an air conditioning system.
[0003]
[Patent Document 1]
JP-A-2003-42084
[0004]
The gas compressor pressurizes the refrigerant gas vaporized by an evaporator for heat exchange by receiving rotational power from the outside, and sends it to a condenser for outdoor heat radiation. FIG. 5 is a cross-sectional view of the gas compressor, and FIG. 6 is a cross-sectional view taken along line AA of FIG.
[0005]
5 and 6, the gas compressor 50 includes a case 52 having a large opening at one end, and a front head 9 also having a large opening at one end. The open ends of the case 52 and the front head 9 are in contact with each other, and have a structure for shutting off the inside and the outside air.
[0006]
Further, the front head 9 has a suction port 51 for sucking a low-pressure refrigerant gas from an evaporator (not shown) connected to the outside, and a suction chamber having a relatively large volume and communicating with the suction port 51. 15 are formed.
[0007]
Further, the gas compressor 50 has the compressor main body 1 inside the case 52 and the front head 9. The compressor body 1 includes a front side block 2, a rear side block 3, a cylinder 4, a rotor 5, a rotating shaft 6, a plurality of vanes 13, and the like.
[0008]
A substantially elliptical cylindrical space is formed inside the cylinder 4. The rotor 5 is rotatably disposed in the center of this space. Both ends of the cylinder 4 are closed by the front side block 2 and the rear side block 3, respectively.
[0009]
The rotor 5 is integrally provided with a rotating shaft 6 penetrating between the end faces. The rotating shaft 6 is rotatably supported by bearing holes 7 and 8 provided in the front side block 2 and the rear side block 3, respectively. Further, a rotating shaft tip side 6 a of the rotating shaft 6 protrudes from the bearing hole 7 and is formed to extend so as to penetrate the front head 9.
[0010]
Further, a seal chamber 10 is provided on the outer periphery of the rotation shaft tip side 6a, and a rotation shaft seal (not shown) is provided in the seal chamber 10. The refrigerating machine oil is supplied to the seal chamber 10 via the bearing gap G between the bearing hole 7 and the rotating shaft 6 during operation of the gas compressor 50.
[0011]
The refrigerating machine oil also acts as a dynamic pressure bearing in the bearing hole 7 supporting the front side block 2 side of the rotating shaft 6 and the bearing hole 8 supporting the rear side block 3 side. That is, pressure is generated in the refrigerating machine oil by viscous friction accompanying rotation of the rotating shaft 6. By this pressure, an oil film of the refrigerating machine oil is formed between the rotating shaft 6 and the two bearing holes 7 and 8, and the rotating shaft 6 is supported by the oil holes without rotating in the bearing holes 7 and 8.
[0012]
Further, a plurality of vane grooves 12 are formed on the outer peripheral surface of the rotor 5 in the radial direction. A vane 13 is slidably mounted in the vane groove 12. The vane 13 is urged against the inner peripheral surface of the cylinder 4 by the centrifugal force and the oil pressure at the bottom of the vane groove 12 when the rotor 5 rotates.
[0013]
Further, the space inside the cylinder 4 is partitioned into a plurality of small chambers by a front side block 2, a rear side block 3, a rotor 5, and vanes 13, 13,. These small chambers are referred to as compression chambers 14, 14..., And the size of the volume is repeatedly changed by the rotation of the rotor 5.
[0014]
When the volume of the compression chambers 14 changes due to rotation of the rotor 5, low-pressure refrigerant gas (hereinafter, referred to as low-pressure refrigerant gas) flows from the suction chamber 15 communicating with the suction port 51 due to the change in volume. The air is sucked into the compression chamber 14 through 41 and is compressed in the compression chamber 14.
[0015]
A discharge hole 16 is formed near the shortest diameter portion of the substantially elliptical opening of the cylinder 4. The discharge hole 16 connects the compression chamber 14 of the cylinder 4 and the discharge valve chamber 45.
Here, the discharge valve chamber 45 includes a cylinder notch 43 in which the outer peripheral surface of the cylinder 4 is cut out in a substantially L-shape outward, the inner surface of the case 52, the front side block 2, the rear side block 3, Means a space surrounded by
[0016]
The head 17a of the reed valve 17 is attached to the discharge valve chamber 45 with a bolt 17c, and its foot 17b covers the discharge hole 16 from the discharge valve chamber 45 side. The reed valve 17 is attached to the discharge valve chamber 45 together with a valve support 17d for regulating the degree of opening of the reed valve 17.
[0017]
Further, the discharge valve chamber 45 is connected to the high-pressure chamber 19 via a discharge passage 44 provided in the rear side block 3. The cyclone block 18 is provided at an outlet of the discharge passage 44 on the high pressure chamber 19 side.
[0018]
The cyclone block 18 separates the refrigerating machine oil from the high-pressure refrigerant gas in which the refrigerating machine oil discharged from the compression chamber 14 is dissolved (hereinafter, referred to as a pre-separation high-pressure refrigerant gas). The high-pressure refrigerant gas from which the refrigerating machine oil has been separated (hereinafter, referred to as a separated high-pressure refrigerant gas) is sent from the discharge port 54 to an external condenser (not shown). The refrigerating machine oil separated by the cyclone block 18 accumulates at the bottom of the high-pressure chamber 19 to form an oil sump 20.
[0019]
On the other hand, around the rotation shaft 6 facing the rotor 5 of the front side block 2 and the rear side block 3, salary grooves 31 and 32 communicating with the bottom of the vane groove 12 are provided.
The refrigerating machine oil is supplied to the Sarai groove 31 from the oil reservoir 20 through the bearing hole 7 through the rear axial oil passage hole 38, the cylinder oil passage hole 36, and the front oil passage hole 37. . The refrigerating machine oil lubricates a sliding portion between the front side block 2 and the rotor 5 and the vane 13, and finally reaches the bottom of the vane groove 12.
[0020]
Here, the rear axial oil passage hole 38 is a hole formed slightly inward of the outermost bottom surface of the rear side block 3 (that is, inside by an O-ring 42R and an O-ring groove 3a to be described later). The rear side block 3 is formed to penetrate along the axial direction (of the rotation shaft 6).
[0021]
The cylinder oil passage hole 36 is a hole formed between the inner peripheral surface and the outer peripheral surface near the bottom of the longest diameter of the substantially elliptical opening of the cylinder 4 and penetrates in the axial direction of the cylinder 4. Have been. The cylinder oil passage hole 36 is connected to a rear axial oil passage hole 38 formed in the rear side block 3.
[0022]
On the other hand, the refrigerating machine oil is also supplied to the Sarai groove 32 from the oil reservoir 20 through the rear radial oil passage hole 39 and the bearing hole 8. The refrigerating machine oil lubricates a sliding portion between the rear side block 3, the rotor 5, and the vane 13.
The rear radial oil passage hole 39 is a hole connected to the rear axial oil passage hole 38 formed in the rear side block 3, and is formed along the radial direction of the rear side block 3.
[0023]
In addition, power from an external drive source such as an engine or a motor (not shown) is transmitted to the pulley 61 via a V-belt 65. A bearing 62 is provided between the pulley 61 and the front head 9.
Further, an armature 63 is fixed to the right end of the rotary shaft tip side 6a, and this armature 63 is attracted or detached from the right end face of the pulley 61 by excitation of the clutch electromagnetic coil 64. When the armature 63 is attracted to the right end face of the pulley 61, the rotor 5 rotates with the rotation of the pulley 61.
[0024]
In such a configuration, a compression stroke in the compression chamber 14 will be described.
In the suction process from the time when the volume of the compression chamber 14 becomes minimum to the maximum, the low-pressure refrigerant gas in the suction chamber 15 is not shown in the suction passage 41 such as the cylinder 4 and the front side block 2 and the rear side block 3 communicating therewith. It is sucked into the compression chamber 14 inside the cylinder 4 via the suction port. When the volume of the compression chamber 14 becomes close to the maximum, the compression chamber 14 separates from the suction port and becomes a closed space, and the low-pressure refrigerant gas is confined in the compression chamber 14.
[0025]
Next, when the volume of the compression chamber 14, which is the closed space, shifts from the maximum to the minimum, the refrigerant gas in the compression chamber 14 is compressed in accordance with the volume reduction. When the volume of the compression chamber 14 becomes close to the minimum, the reed valve 17 covering the discharge hole 16 of the cylinder 4 is opened by the pressure of the compressed refrigerant gas.
[0026]
Then, the high-pressure refrigerant gas in the compression chamber 14 is discharged to the discharge valve chamber 45. The pre-separation high-pressure refrigerant gas discharged into the discharge valve chamber 45 reaches the high-pressure chamber 19 via the discharge passage 44, and after the refrigerating machine oil is separated in the cyclone block 18, the separated high-pressure refrigerant gas is used as an external condenser after the separation. Sent to
[0027]
Note that, in the gas compressor 50, since there are two suction ports for sucking the refrigerant gas into the compression chamber 14 in the cylinder 4 and there are five vanes 13, the above-described refrigerant gas is rotated during one rotation of the rotor 5. Is performed alternately five times, for a total of ten times.
On the other hand, the refrigerating machine oil separated by the cyclone block 18 is pressure-fed from the oil sump 20 to each sliding portion of the gas compressor 50 according to the pressure difference when the rotor 5 rotates.
[0028]
[Problems to be solved by the invention]
Incidentally, in the case of the gas compressor 50, as described above, the high-pressure refrigerant gas before separation compressed in the compression chamber 14 is discharged to the discharge valve chamber 45. The discharge valve chamber 45 is a space surrounded by the cylinder cutout 43, the inner surface of the case 52, the front side block 2, and the rear side block 3 (that is, the discharge valve chamber 45 Open space).
[0029]
Therefore, the pre-separation high-pressure refrigerant gas discharged into the discharge valve chamber 45 and the pre-separation high-pressure refrigerant gas existing in the gap 4a between the outer peripheral surface of the cylinder 4 and the inner surface of the case 52 are not connected to the front side block 2 or the rear side block 3. There is a possibility that the gas may flow out from the boundary with the inner surface of the case 52 to the suction chamber 15 side or the high-pressure chamber 19 side.
[0030]
In particular, when the high pressure refrigerant gas before separation discharged to the discharge valve chamber 45 on the side of the rear side block 3 flows out to the high pressure chamber 19 without separating the refrigeration oil in the cyclone block 18, the refrigeration oil is directly compressed by the gas compressor. There is a possibility that the gas may flow out of the gas compressor 50 and the lubrication inside the gas compressor 50 may be insufficient. For this reason, an O-ring 42R is conventionally attached to the outer peripheral surface of the rear side block 3 on the case 52 side.
[0031]
However, since the O-ring 42R is used in a high-pressure space on the high-pressure chamber 19 side, in addition to high pressure resistance and high heat resistance, corrosion resistance to refrigerant gas and refrigerating machine oil is required, and it is necessary to use an expensive material. there were.
Further, in order to attach the O-ring 42R to the rear side block 3, it is necessary to form an O-ring groove 3a in the rear side block 3, but the shape of the O-ring groove 3a depends on the diameter of the O-ring 42R, the rear side block 3, and Since it is determined in consideration of the expansion coefficient and the like of the case 52, it is necessary to perform processing with high accuracy.
[0032]
In addition, the inner surface of the case 52 has a wide area (for example, B in the figure) in consideration of the expansion rate of the rear side block 3 and the case 52 in order to increase the airtightness between the rear side block 3 and the case 52. It was necessary to process with high precision over the range shown).
Therefore, it is difficult to reduce the material cost of the O-ring 42R and the processing cost of the O-ring groove 3a or the inner surface of the case 52, and as a result, it is also difficult to reduce the manufacturing cost of the gas compressor 50.
[0033]
The present invention has been made in view of such conventional problems, and an object of the present invention is to provide a gas compressor that can reduce manufacturing costs by eliminating an O-ring attached to a rear side block.
[0034]
[Means for Solving the Problems]
For this reason, the present invention provides a cylinder housed in a case, a rotor disposed in the cylinder, a compression chamber in which refrigerant gas is compressed by rotation of the rotor, and a refrigerant gas compressed in the compression chamber. Discharged, and a discharge valve chamber formed in a space that is not communicated with the gap between the case and the cylinder, a discharge passage through which refrigerant gas discharged to the discharge valve chamber passes, and the discharge passage A cyclone block for separating refrigeration oil from the passed refrigerant gas, and a high-pressure chamber for storing the refrigerant gas from which the refrigeration oil was separated by the cyclone block were provided.
[0035]
There is a gap between the case and the cylinder due to the interior. The discharge valve chamber from which the refrigerant gas compressed in the compression chamber is discharged is formed as a space not communicating with the gap. Accordingly, the refrigerant gas discharged to the discharge valve chamber does not flow out of the boundary between the rear side block and the inner surface of the case to the high pressure chamber side without passing through the cyclone block.
Therefore, it is not necessary to attach an O-ring to the rear side block in order to maintain the airtightness between the rear side block and the inner surface of the case. Therefore, the material cost of the O-ring conventionally required can be eliminated.
[0036]
Further, since there is no need to attach an O-ring to the rear side block, there is no need to form an O-ring groove in the rear side block. Accordingly, the cost required for processing the O-ring groove can be eliminated.
Further, also on the inner surface of the case, there is no need for airtightness between the rear side block and the case, so that high-precision processing is not required. Therefore, the cost required for processing the inner surface of the case can be reduced.
[0037]
As a result, the material cost of the O-ring and the processing cost of the O-ring groove can be eliminated, and the processing cost of the inner surface of the case can be reduced, so that the manufacturing cost of the gas compressor can be reduced.
[0038]
Further, in the present invention, the discharge valve chamber is a space including a passage hole formed between an outer peripheral surface that is the case-side surface and an inner peripheral surface that is the rotor-side surface in the cylinder. It is characterized by the following.
[0039]
By forming the discharge valve chamber as a passage hole inside the cylinder, for example, refrigerant gas can be prevented from leaking from the passage hole into the gap between the case and the cylinder. With the passage hole, the processing cost for forming the discharge valve chamber can be reduced.
[0040]
Further, the present invention includes a front side block and a rear side block that sandwich the cylinder, wherein the passage hole is a hole that penetrates in an axial direction of the rotor of the cylinder, and the discharge valve chamber includes the passage hole. And a space surrounded by the front side block and the rear side block.
[0041]
The discharge valve chamber is partitioned as a closed space using a boundary surface between the cylinder and the rear side block or the like. This makes it difficult for the refrigerant gas to leak from the passage hole into the gap between the case and the cylinder.
[0042]
Further, the present invention includes an oil sump in which the refrigerating machine oil separated by the cyclone block is stored, and refrigerating machine oil supply means for supplying the refrigerating machine oil from the oil sump to an internal sliding portion, The supply means has an oil passage surrounded by at least an inner surface of the case and an outer peripheral surface of the cylinder.
[0043]
By partitioning the discharge valve chamber as a closed space, there is no refrigerant gas before passing through the cyclone block discharged to the discharge valve chamber between the inner surface of the case and the outer peripheral surface of the cylinder.
Thus, the portion surrounded by the inner surface of the case and the outer peripheral surface of the cylinder can be used as an oil passage to supply the refrigerating machine oil.
[0044]
Further, the present invention is characterized in that the oil passage is a groove or a space formed on an outer peripheral surface of the cylinder and / or an inner surface of the case.
[0045]
The oil passage exists on the outer peripheral surface side of the cylinder. Therefore, the distance between the oil passage and the compression chamber in the cylinder can be increased.
Therefore, since the refrigerating machine oil is less likely to leak from the oil passage into the compression chamber, the performance of the gas compressor, such as power efficiency and volumetric efficiency, can be improved.
[0046]
Further, the present invention is characterized in that the oil passage is a gap between a flat surface of an outer peripheral surface of the cylinder and an inner surface of the case.
[0047]
Thus, stress concentration on the cylinder due to the formation of the oil passage can be avoided.
[0048]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described. FIG. 1 is a cross-sectional view of a gas compressor according to a first embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along line CC of FIG. 5 and 6 are denoted by the same reference numerals, and description thereof will be omitted.
1 and 2, the gas compressor 150 includes a case 152 (not shown) in which the inner surface is not machined as much as the case 52 (not shown) instead of the case 52 in which the inner surface is machined with high accuracy (conventional). Have.
[0049]
The gas compressor 150 has the compressor body 101 inside the case 152 and the front head 9. The compressor main body 101 includes a front side block 2, a rear side block 103, a cylinder 104, a rotor 5, a rotating shaft 6, a plurality of vanes 13, and the like.
[0050]
Further, unlike the rear side block 3 of the conventional gas compressor 50, the rear side block 103 does not have the O-ring 42R attached to the outer peripheral surface on the case 152 side. Further, since the O-ring 42R is not attached, no O-ring groove is formed on the outer peripheral surface thereof.
On the other hand, a reed valve 117 and the like are attached to the rear side block 103 as described later.
[0051]
Further, a substantially elliptical cylindrical space is formed inside the cylinder 104 as in the related art. A discharge hole 16 is also formed near the shortest diameter portion of the substantially elliptical opening, as in the related art, so that the compression chamber 14 and the discharge valve chamber 145 communicate with each other.
[0052]
Here, the discharge valve chamber 145 is formed between the inner peripheral surface and the outer peripheral surface of the cylinder 104 (instead of the cylinder notch 43 of the conventional cylinder 4), and penetrates in the axial direction of the cylinder 104. Of the cylinder passage hole 143, the front side block 2, and the rear side block 103. Therefore, the discharge valve chamber 145 can prevent the refrigerant gas from leaking from the cylinder passage hole 143 into the gap 104a between the case 152 and the cylinder 104.
[0053]
The discharge valve chamber 145 is connected to the high-pressure chamber 19 via a discharge passage 144 provided in the rear side block 103, as in the related art. A cyclone block 18 is also provided at the outlet of the discharge passage 144 on the high pressure chamber 19 side, as in the conventional case.
[0054]
The head 117a of the reed valve 117 is attached to the discharge passage 144 of the rear side block 103 with a bolt 117c. The foot 117 b of the reed valve 117 extends from the discharge passage 144 to the discharge valve chamber 145, and covers the discharge hole 16. Further, the reed valve 117 is attached to the discharge passage 144 of the rear side block 103 together with a valve support 117d for regulating the degree of opening of the reed valve 117.
[0055]
At this time, in FIG. 1, the discharge side end of the discharge hole 16 is formed slightly inclined toward the front side block 2. Therefore, the refrigerant gas in the compression chamber 14 is discharged toward the foot 117 b of the reed valve 117 attached to the rear side block 103.
[0056]
Therefore, the refrigerant gas in the compression chamber 14 flows out smoothly to the discharge valve chamber 145, and an increase in the power of the gas compressor 150 can be prevented. Further, the discharge hole 16 having such a shape can be easily formed by processing the hole from the inside of the cylinder 104.
[0057]
On the other hand, around the rotary shaft 6 facing the rotor 5 of the front side block 2 and the rear side block 103, sali grooves 31 and 32 communicating with the bottoms of the vane grooves 12, respectively, are provided as in the related art.
The rear side block 103 has a rear axial oil passage groove 138 instead of the rear axial oil passage hole 38 formed in the conventional rear side block 3. The rear axial oil passage groove 138 is a groove formed on the outermost bottom surface of the rear side block 103, and is formed along the axial direction of the rear side block 103.
[0058]
In the cylinder 104, a cylinder oil passage groove 136 is formed instead of the cylinder oil passage hole 36 formed in the conventional cylinder 4. The cylinder oil passage groove 136 is also a groove formed on the outer peripheral surface near the bottom of the longest diameter of the substantially elliptical opening of the cylinder 104, and is formed along the axial direction of the cylinder 104. The cylinder oil passage groove 136 is connected to a rear axial oil passage groove 138 formed in the rear side block 103, and has a semicircular cross section in the radial direction.
[0059]
In the case of the gas compressor 150 of the present embodiment, as described later, refrigerating machine oil exists in a gap 104a between the outer peripheral surface of the cylinder 104 and the inner surface of the case 152. The gap 104a has the same atmosphere as the atmosphere in the high-pressure chamber 19 (as shown in FIG. 2, the liquid level 20a of the refrigerating machine oil can be seen in the gap 104a).
[0060]
In such a configuration, when the volume of the compression chamber 14 becomes close to the minimum, the reed valve 117 covering the discharge hole 16 of the cylinder 104 is opened by the pressure of the compressed refrigerant gas as in the related art. Then, the high-pressure refrigerant gas in the compression chamber 14 is discharged to the discharge valve chamber 145.
[0061]
At this time, as described above, the refrigerant gas in the compression chamber 14 is moved toward the foot 117b by the inclination of the discharge hole 16 toward the front side block 2 and the attachment of the reed valve 117 to the rear side block 103. To be discharged. Therefore, an increase in the power of the gas compressor 150 can be prevented.
[0062]
The pre-separation high-pressure refrigerant gas discharged into the discharge valve chamber 145 reaches the high-pressure chamber 19 via the discharge passage 144, and the refrigerating machine oil is separated in the cyclone block 18.
Since the discharge valve chamber 145 is not communicated with the gap 104a between the case 152 and the cylinder 104, it is not necessary to attach the O-ring 42R to the rear side block 103 or to process the inner surface of the case 152 with high precision. The high pressure refrigerant gas before separation discharged to the discharge valve chamber 145 does not flow out to the high pressure chamber 19 side from the boundary between the rear side block 103 and the inner surface of the case 152. Therefore, all the high pressure refrigerant gas before separation discharged into the discharge valve chamber 145 is separated from the refrigerating machine oil by the cyclone block 18.
[0063]
Here, in the case of the present embodiment, it is necessary to consider the possibility that the pre-separation high-pressure refrigerant gas flows out of the discharge valve chamber 145 to the high-pressure chamber 19 through the boundary surface between the cylinder 104 and the rear side block 103 and the like. However, the boundary surface between the cylinder 104 and the rear side block 103 is inherently in metal contact with high airtightness in order to realize separation or the like between the suction passage 41 and the compression chamber 14. Plane. Therefore, as long as the refrigerant gas sucked into the compression chamber 14 is compressed without leaking into the suction passage 41 and the like, the high-pressure refrigerant gas before separation does not flow out of the discharge valve chamber 45 to the high-pressure chamber 19 side. .
[0064]
On the other hand, the refrigerating machine oil separated by the cyclone block 18 is pressure-fed from the oil sump 20 to each sliding portion in the gas compressor 150 in accordance with the pressure difference at the time of rotation of the rotor 5 as in the related art.
At this time, since the cylinder oil passage groove 136 is formed on the outer peripheral surface of the cylinder 104, the distance 135a to the compression chamber 14 is longer than the distance 35a of the conventional gas compressor 50.
[0065]
Here, the distance 135a means a distance between the cylinder oil passage groove 136 and the compression chamber 14 closest to the cylinder oil passage groove 136 at both ends of the cylinder 104. Further, the distance 35a also refers to the distance between the cylinder oil passage hole 36 and the compression chamber 14 closest to the cylinder oil passage hole 36 in the conventional gas compressor 50 (FIGS. 5 and 6). The distance 135a and the distance 35a are both distances for preventing the refrigerating machine oil in the cylinder oil passage groove 136 (or the cylinder oil passage hole 36) from flowing out to the compression chamber 14.
[0066]
However, in the conventional gas compressor 50, since the pre-separation high-pressure refrigerant gas was present in the gap 4a, it was necessary to seal not only the compression chamber 14 but also the gap 4a (that is, the gap 4a). It was also necessary to provide a distance 35b for the gap 4a). Therefore, in order to secure a long distance 35b to the gap 4a, the distance 35a to the compression chamber 14 has to be reduced.
[0067]
On the other hand, in the gas compressor 150 of the present embodiment, the discharge valve chamber 145 is a space closed with respect to the case 152. Therefore, the pre-separation high-pressure refrigerant gas does not exist in the gap 104 a between the outer peripheral surface of the cylinder 104 and the inner surface of the case 152. Since the O-ring 42R is not attached to the rear side block 103, the gap 104a has the same atmosphere as the atmosphere in the high-pressure chamber 19. Therefore, in the gas compressor 150 of the present embodiment, only the sealing with respect to the compression chamber 14 needs to be performed, and the long distance 135a can be ensured.
[0068]
As described above, since the discharge valve chamber 145 into which the pre-separation high-pressure refrigerant gas is discharged is a closed space with respect to the case 152, the pre-separation high-pressure refrigerant gas is separated from the boundary between the rear side block 103 and the inner surface of the case 152. Does not flow directly to the high-pressure chamber 19 side.
[0069]
Therefore, it is not necessary to attach the O-ring 42R to the rear side block 103 in order to maintain the airtightness between the rear side block 103 and the inner surface of the case 152. Therefore, the material cost required for the O-ring 42R can be eliminated.
Further, since there is no need to attach the O-ring 42R to the rear side block 103, there is no need to form the O-ring groove 3a in the rear side block 103. Therefore, the cost required for machining the O-ring groove of the rear side block 103 can be eliminated.
[0070]
Furthermore, the airtightness between the rear side block 103 and the case 152 is not required on the inner surface of the case 152, so that high-precision processing is not required. Therefore, the cost required for processing the inner surface of the case 152 can be reduced.
As a result, the material cost of the O-ring 42R and the processing cost of the O-ring groove 3a can be eliminated, and the processing cost of the inner surface of the case 52 can be reduced, so that the manufacturing cost of the gas compressor 150 can be reduced. Can be.
[0071]
Further, since the discharge valve chamber 145 can be made a closed space with respect to the case 152 by using the cylinder passage hole 143 formed in the cylinder 104, the processing cost for forming the discharge valve chamber 145 can be reduced. Can be.
[0072]
On the other hand, the refrigerating machine oil in the oil sump 20 is pressure-fed to each sliding portion in the gas compressor 150 via the rear axial direction oil passage groove 138, the cylinder oil passage groove 136, and the like. Therefore, the distance 135a between the cylinder oil passage groove 136 and the compression chamber 14 can be increased.
[0073]
Therefore, since the refrigerating machine oil is less likely to leak from the cylinder oil passage groove 136 to the compression chamber 14, the performance of the gas compressor 150, such as power efficiency and volumetric efficiency, can be improved.
Further, since the rear axial direction oil passage groove 138 and the cylinder oil passage groove 136 can be formed by a mold, the processing cost can be reduced.
[0074]
In the present embodiment, the cylinder oil passage groove 136 having a semicircular cross section has been described as being formed in the rear side block 103. However, the present invention is not limited to this, and a groove having a rectangular cross section may be formed.
[0075]
Further, in the present embodiment, the description has been made assuming that the rear axial oil passage groove 138 and the cylinder oil passage groove 136 are formed in the rear side block 103 and the cylinder 104, but the invention is not limited to this. That is, the outermost peripheral bottom surface of the rear side block 103 and the outer peripheral surface near the longest diameter bottom portion of the cylinder 104 are flattened horizontally, and the gap between the flattened surface and the inner surface of the case 152 is formed by the rear axial oil passage groove 138 or the like. It may be used instead of the cylinder oil passage groove 136 (not shown).
[0076]
In particular, by flattening the outer peripheral surface of the cylinder 104 and substituting the cylinder oil passage groove 136, the stress applied to the cylinder 104 can be prevented from being concentrated near the cylinder oil passage groove 136.
Instead of forming the cylinder oil passage groove 136 or the like or flattening, the gap 104a itself may be enlarged (not shown).
[0077]
Next, a second embodiment of the present invention will be described.
In the gas compressor 150 according to the first embodiment, the rear axial oil passage groove 138 and the cylinder oil passage groove 136 are formed on the rear side block 103 and the cylinder 104 side. Reference numeral 250 denotes a groove formed on the inner surface of the case 252.
[0078]
FIG. 3 is a cross-sectional view of a gas compressor according to a second embodiment of the present invention, and FIG. 4 is a cross-sectional view taken along line DD of FIG. 1 and 2 are denoted by the same reference numerals and description thereof is omitted.
3 and 4, a case oil passage groove 253 is formed on the inner surface of the bottom of the case 252 of the gas compressor 250. The case oil passage groove 253 is formed along the axial direction of the case 252 (with respect to the rotation shaft 6).
[0079]
The case oil passage groove 253 is formed from a position where the oil reservoir 20 is formed to a position where the front side block 2 is attached (that is, a portion where the rear side block 103 and the cylinder 204 are arranged).
On the other hand, the rear side block 203 and the cylinder 204 in the compressor main body 201 are not provided with the rear axial oil passage groove 138, the cylinder oil passage groove 136, and the like.
[0080]
In such a configuration, the refrigerating machine oil in the oil sump 20 is filled with a gap between the case oil passage groove 253 formed on the inner surface of the case 252 and the outer peripheral surface of the rear side block 103, and between the case oil passage groove 253 and the outer peripheral surface of the cylinder 104. The pressure is fed to the front oil passage hole 37 through the gap.
[0081]
At this time, since the rear axial oil passage groove 138 and the cylinder oil passage groove 136 are not formed in the rear side block 203 and the cylinder 204, the distance 235a can be further increased.
Therefore, performance such as power efficiency and volume efficiency of the gas compressor 250 can be further improved.
[0082]
Here, the rear side block 203 and the cylinder 204 have been described as not having the rear axial oil passage groove 138 and the cylinder oil passage groove 136 formed therein, but of course, in order to secure a wide passage for the refrigerating machine oil. The case oil passage groove 253, the rear axial oil passage groove 138, and the cylinder oil passage groove 136 may be formed.
[0083]
【The invention's effect】
As described above, according to the present invention, since the discharge valve chamber is configured as a space that is not communicated with the gap between the case and the cylinder, the O-ring conventionally attached to the rear side block can be eliminated, and The manufacturing cost of the compressor can be reduced.
In addition, this allows a portion surrounded by the inner surface of the case and the outer peripheral surface of the cylinder to be configured as an oil passage, so that refrigerating machine oil is less likely to leak from the oil passage into the compression chamber, and the power efficiency, volume efficiency, etc. of the gas compressor. Performance can be improved.
[Brief description of the drawings]
FIG. 1 is a sectional view of a gas compressor according to a first embodiment of the present invention.
FIG. 2 is a sectional view taken along the line CC in FIG.
FIG. 3 is a sectional view of a gas compressor according to a second embodiment of the present invention.
FIG. 4 is a sectional view taken along line DD in FIG. 3;
FIG. 5 is a cross-sectional view of a conventional gas compressor.
FIG. 6 is a sectional view taken along the line AA in FIG. 5;
[Explanation of symbols]
2 Front side block
3, 103, 203 Rear side block
4, 104, 204 cylinders
5 Rotor
6 Rotation axis
14 Compression chamber
18 Cyclone Block
19 High-pressure chamber
44, 144 discharge passage
45, 145 discharge valve chamber
50, 150, 250 Gas compressor
52, 152, 252 cases
136 Cylinder oil passage groove
138 Rear axial oil passage groove
143 Cylinder passage hole
253 Case oil passage groove

Claims (6)

A cylinder inside the case,
A rotor disposed in the cylinder;
A compression chamber in which refrigerant gas is compressed by rotation of the rotor,
A discharge valve chamber formed by a space in which the refrigerant gas compressed in the compression chamber is discharged, and which is not communicated with a gap between the case and the cylinder;
A discharge passage through which the refrigerant gas discharged into the discharge valve chamber passes;
A cyclone block that separates refrigerating machine oil from the refrigerant gas that has passed through the discharge passage;
A high-pressure chamber for storing refrigerant gas from which refrigerating machine oil has been separated by the cyclone block. The discharge valve chamber,
The gas compression according to claim 1, wherein the cylinder includes a space including a passage hole formed between an outer peripheral surface that is the case-side surface and an inner peripheral surface that is the rotor-side surface. Machine. A front side block and a rear side block that sandwich the cylinder,
The passage hole,
A hole penetrating in the axial direction of the rotor of the cylinder,
The discharge valve chamber,
The gas compressor according to claim 2, wherein the space is a space surrounded by the passage hole, the front side block, and the rear side block. An oil reservoir in which the refrigerating machine oil separated in the cyclone block is stored,
Refrigerating machine oil supply means for supplying the refrigerating machine oil from the oil sump to an internal sliding portion,
4. The gas compressor according to claim 1, wherein the refrigerating machine oil supply means has an oil passage surrounded by at least an inner surface of the case and an outer peripheral surface of the cylinder. The oil passage,
The gas compressor according to claim 4, wherein the gas compressor is a groove or a space formed on an outer peripheral surface of the cylinder and / or an inner surface of the case. 5. The gas compressor according to claim 4, wherein the oil passage is a gap between a flat surface of an outer peripheral surface of the cylinder and an inner surface of the case. 6.

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