JP2009281304A - Rotary compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To restrict the distortion of a cylinder while holding air tightness between an inner circumferential surface of an intake passage and an outer circumferential surface of an inlet tube. <P>SOLUTION: The rotary compressor is provided with a front cylinder 33 housed in a sealed casing 10, and having a cylinder chamber S1 and an intake passage 33c connected to the cylinder S1, a branch tube 42a to supply a CO<SB>2</SB>cooling medium from the outer side of the sealed casing 10 to the cylinder chamber S1, the inlet tube 60a having one end connected to the intake passage 33c, the other end connected to the branch tube 42a, and a groove 64a formed along the circumference on an outer circumferential surface at one end, and a circular O-ring 70a installed on the groove 64 of the inlet tube 60a to seal the outer circumferential surface of one end of the inlet tube 60a and the inner circumferential surface of the intake passage 33c of the cylinder 33. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rotary compressor including a seal member that seals between an outer peripheral surface of an inlet tube and an inner peripheral surface of a suction passage of a cylinder.

  In recent years, various rotary compressors that compress refrigerant by rotating a roller mounted on a rotating shaft in a cylinder chamber of a cylinder have been developed. The refrigerant compressed in the rotary compressor is supplied from a suction pipe provided outside the sealed casing to the cylinder chamber via an inlet tube connected to a suction passage communicating with the cylinder chamber (for example, Patent Documents). 1).

Patent Document 1 discloses a compressor in which an inlet tube that is press-fitted into a suction passage that communicates with a cylinder chamber is connected to a tip of a suction pipe that extends from a lower portion of a gas-liquid separator. In the compressor disclosed in Patent Document 1, an O-ring is provided in a groove formed in the inner peripheral surface of the suction passage of the cylinder so that the inner peripheral surface of the suction passage and the outer peripheral surface of the inlet tube are sealed. It is joined.
JP-A-9-287853

However, the compressor disclosed in Patent Document 1 has a disadvantage in that the rigidity of the cylinder is lowered because the groove for attaching the O-ring is formed in the cylinder. In particular, in the case of using a CO ₂ refrigerant, which has been attracting attention because of its small impact on global warming, the inside of the sealed casing becomes high pressure, so that cylinder distortion becomes noticeable.

  Accordingly, the present invention has been made to solve the above-described problems, and can suppress the distortion of the cylinder while keeping the inner peripheral surface of the suction passage and the outer peripheral surface of the inlet tube airtight. Is to provide a simple rotary compressor.

  A rotary compressor according to a first aspect of the present invention provides a sealed casing, a cylinder housed in the sealed casing, having a cylinder chamber and a suction passage communicating with the cylinder chamber, and supplying refrigerant to the cylinder chamber from the outside of the sealed casing An inlet tube having one end connected to the suction passage, the other end connected to the suction tube, and a groove formed along the circumferential direction on the outer peripheral surface of the one end, and an inlet An annular seal member is provided which is attached to the groove portion of the tube and seals between the outer peripheral surface of one end of the inlet tube and the inner peripheral surface of the suction passage of the cylinder.

In this rotary compressor, it is necessary to form a groove in the cylinder by forming a groove in the inlet tube for mounting a seal member that seals between the inner peripheral surface of the suction passage and the outer peripheral surface of the inlet tube. Therefore, the cylinder rigidity can be prevented from being lowered. In particular, in the case of a compressor using a CO ₂ refrigerant, since the inside of the hermetic casing becomes a high pressure and distortion of the cylinder appears remarkably, it is very effective to prevent the cylinder rigidity from being lowered as in the present invention. It is. In this manner, the cylinder can be prevented from being distorted while the inner peripheral surface of the suction passage and the outer peripheral surface of the inlet tube are hermetically held by the seal member.

  Further, in this rotary compressor, the process of forming the groove on the outer peripheral surface of the inlet tube is easier than the process of forming the groove on the inner peripheral surface of the suction passage of the cylinder. While being able to suppress, it can suppress that a process becomes complicated.

  In this rotary compressor, since the groove portion is formed on the outer peripheral surface of the inlet tube, the groove portion can be easily cleaned as compared with the case where the groove portion is formed on the inner peripheral surface of the suction passage of the cylinder. Thereby, the rotary compressor excellent in maintainability can be obtained.

  Further, in this rotary compressor, one end of the inlet tube can be connected to the suction passage of the cylinder in a state where the seal member is mounted in the groove formed on the outer peripheral surface of the inlet tube. For this reason, it can suppress that the said sealing member is damaged with an inlet tube.

  A rotary compressor according to a second invention is the rotary compressor according to the first invention, wherein the seal member is hydrogenated nitrile rubber.

  In this rotary compressor, by using a seal member made of hydrogenated nitrile rubber having oil resistance and heat resistance, high temperature oil supplied to each sliding portion of the compressor and compressed high temperature refrigerant exist. Even under the influence, deterioration of the seal member can be suppressed. Thereby, the rotary compressor excellent in maintainability can be obtained.

  A rotary compressor according to a third invention is the rotary compressor according to the first or second invention, wherein a joint pipe for holding the inlet tube is fixed to the hermetic casing, and the inner peripheral surface of the joint pipe The other end of the inlet tube is joined to the outer peripheral surface by brazing.

  In this rotary compressor, as described above, since it is easy to process the groove portion, it is possible to form the groove portion at a desired location, so that it is away from the joint location related to brazing between the joint pipe and the inlet tube. It becomes possible to form a groove part in a location. Thereby, even when brazing a joint pipe and an inlet tube, since heat by the brazing becomes difficult to reach the seal member, it is possible to suppress the seal member from being deformed by the heat.

  A rotary compressor according to a fourth invention is the rotary compressor according to any one of the first to third inventions, wherein the outer diameter of one end of the inlet tube is smaller than the outer diameter of the other end of the inlet tube.

  In this rotary compressor, by making the outer diameter of one end of the inlet tube connected to the suction passage smaller than the outer diameter of the other end, the inner diameter of the suction passage connected to the one end can be reduced. As a result, it is possible to suppress a decrease in the rigidity of the cylinder due to the formation of the suction passage.

  A rotary compressor according to a fifth invention is the rotary compressor according to any one of the first to fourth inventions, wherein the suction passage of the cylinder includes a large-diameter passage into which one end of the inlet tube is inserted, and the large-diameter passage. And a small diameter passage having an inner diameter smaller than that of the diameter passage.

  In this rotary compressor, by providing a large-diameter passage into which one end of the inlet tube is inserted, the inner diameter of the inlet tube inserted into the large-diameter passage can be made equal to the inner diameter of the small-diameter passage. Become. As a result, the refrigerant flow between the inlet tube and the suction passage can be smoothly passed without being disturbed.

  A rotary compressor according to a sixth aspect of the present invention is the rotary compressor according to any one of the first to fifth aspects of the invention, wherein the tip of one end of the inlet tube has a tapered shape.

  In this rotary compressor, by making the tip of one end of the inlet tube into a tapered shape, it becomes easy to insert the one end of the inlet tube into the suction passage, and the sealing member can be easily attached to the groove.

  A rotary compressor according to a seventh aspect of the present invention is a sealed casing, a first cylinder housed in the sealed casing, having a first cylinder chamber and a first suction passage communicating with the first cylinder chamber, and a sealed casing. A second cylinder housed therein and having a second cylinder chamber and a second suction passage communicating with the second cylinder chamber; a first branch pipe for supplying refrigerant to the first cylinder chamber from the outside of the sealed casing; And a suction pipe assembly having a second branch pipe for supplying refrigerant to the second cylinder chamber from the outside of the hermetic casing, one end connected to the first suction passage, and the other connected to the first branch pipe The first inlet tube having a first groove portion formed along the circumferential direction on the end and the outer peripheral surface of the one end, one end connected to the second suction passage, and connected to the second branch pipe And a second inlet tube having a second groove formed along the circumferential direction on the outer peripheral surface of the one end, and a first groove of the first inlet tube. An annular first seal member that seals between the outer peripheral surface at one end and the inner peripheral surface of the first suction passage of the first cylinder, and a second groove portion of the second inlet tube, are attached to the second inlet. An annular second seal member is provided for sealing between the outer peripheral surface at one end of the tube and the inner peripheral surface of the second suction passage of the second cylinder.

In this rotary compressor, the first groove for mounting the first seal member for sealing between the inner peripheral surface of the first suction passage and the outer peripheral surface of the first inlet tube, and the inner periphery of the second suction passage Forming a second groove for mounting a second seal member for sealing between the surface and the outer peripheral surface of the second inlet tube in the first and second inlet tubes, respectively. There is no need to form a groove, and the rigidity of the first and second cylinders can be prevented from decreasing. Particularly, in the case of a compressor using a CO ₂ refrigerant, the inside of the hermetic casing becomes a high pressure, and the distortion of the first and second cylinders appears remarkably, so that the rigidity of the first and second cylinders decreases as in the present invention. It is very effective to prevent this. In this manner, the inner peripheral surface of the first suction passage and the outer peripheral surface of the first inlet tube are hermetically held by the first seal member, and the inner peripheral surface of the second suction passage and the outer peripheral surface of the second inlet tube. Can be held airtight by the second seal member, and distortion of the first and second cylinders can be suppressed.

  In this rotary compressor, the process of forming the first and second groove portions on the outer peripheral surfaces of the first and second inlet tubes is easier than the process of forming the groove portions on the inner peripheral surface of the suction passage. And it can suppress that processing cost increases, and can suppress that processing becomes complicated.

  Further, in this rotary compressor, since the first and second groove portions are formed on the outer peripheral surfaces of the first and second inlet tubes, compared to the case where the groove portion is formed on the inner peripheral surface of the suction passage of the cylinder, The cleaning of the first and second groove portions can be performed easily. Thereby, the rotary compressor excellent in maintainability can be obtained.

  Further, in this rotary compressor, one end of the first inlet tube is connected to the suction passage of the first cylinder in a state where the first seal member is mounted in the first groove formed on the outer peripheral surface of the first inlet tube. At the same time, one end of the second inlet tube can be connected to the suction passage of the second cylinder in a state in which the second seal member is mounted in the second groove formed on the outer peripheral surface of the second inlet tube. For this reason, it can suppress that the said 1st and 2nd sealing member is damaged by the 1st and 2nd inlet tube.

  As described above, according to the present invention, the following effects can be obtained.

In the first and seventh aspects, a groove is formed in the cylinder by forming a groove in the inlet tube for mounting a seal member that seals between the inner peripheral surface of the suction passage and the outer peripheral surface of the inlet tube. Therefore, it is possible to prevent the cylinder rigidity from being lowered. In particular, in the case of a compressor using a CO ₂ refrigerant, since the inside of the hermetic casing becomes a high pressure and distortion of the cylinder appears remarkably, it is very effective to prevent the cylinder rigidity from being lowered as in the present invention. It is. In this manner, the cylinder can be prevented from being distorted while the inner peripheral surface of the suction passage and the outer peripheral surface of the inlet tube are kept airtight by the seal member.
In addition, since the process of forming the groove on the outer peripheral surface of the inlet tube is easier than the process of forming the groove on the inner peripheral surface of the suction passage of the cylinder, an increase in processing cost can be suppressed. , It is possible to prevent the processing from becoming complicated.
Further, since the groove portion is formed on the outer peripheral surface of the inlet tube, the groove portion can be easily cleaned compared with the case where the groove portion is formed on the inner peripheral surface of the suction passage of the cylinder. Thereby, the rotary compressor excellent in maintainability can be obtained.
Further, one end of the inlet tube can be connected to the suction passage of the cylinder in a state where the seal member is mounted in the groove formed on the outer peripheral surface of the inlet tube. For this reason, it can suppress that the said sealing member is damaged with an inlet tube.

  In the second invention, the deterioration of the seal member can be suppressed even under the influence of high-temperature oil supplied to each sliding portion of the compressor or compressed high-temperature refrigerant. it can. Thereby, the rotary compressor excellent in maintainability can be obtained.

  Further, in the third invention, even when the joint pipe and the inlet tube are brazed, the heat due to the brazing becomes difficult to reach the seal member, so that the seal member is prevented from being deformed by the heat. it can.

  In the fourth aspect of the invention, by reducing the outer diameter of one end of the inlet tube connected to the suction passage from the outer diameter of the other end, the inner diameter of the suction passage connected to the one end can be reduced. it can. As a result, it is possible to suppress a decrease in the rigidity of the cylinder due to the formation of the suction passage.

  In the fifth invention, the inner diameter of the inlet tube inserted into the large diameter passage and the inner diameter of the small diameter passage can be made equal. As a result, the refrigerant flow between the inlet tube and the suction passage can be smoothly passed without being disturbed.

  In the sixth aspect of the invention, it is easy to insert one end of the inlet tube into the suction passage, and it is easy to attach the seal member to the groove.

Hereinafter, an embodiment of a rotary compressor for a CO ₂ refrigerant according to the present invention will be described based on the drawings.

FIG. 1 is a cross-sectional view showing the internal structure of a two-cylinder rotary compressor for CO ₂ refrigerant according to an embodiment of the present invention. 2 is a plan view showing a front head of the rotary compressor shown in FIG. 1, and FIG. 3 is a plan view showing a front cylinder and a piston of the rotary compressor shown in FIG. 4 is a cross-sectional view taken along line AA in FIG. FIG. 5 is a cross-sectional view showing a connection structure of a branch pipe, an inlet tube and a cylinder of the suction pipe assembly of the rotary compressor shown in FIG. 6 is a cross-sectional view showing an inlet tube of the rotary compressor shown in FIG. 1, and FIG. 7 is a plan view and (b) showing an O-ring of the rotary compressor shown in FIG. It is a front view. Hereinafter, the CO ₂ refrigerant rotary compressor 1 according to an embodiment of the present invention will be described in detail with reference to FIGS.

As shown in FIG. 1, the CO ₂ refrigerant rotary compressor 1 is a two-cylinder rotary compressor. And a suction pipe assembly 40 disposed on the side of the casing 10. The rotary compressor 1 is a so-called high-pressure dome type compressor and uses a CO ₂ refrigerant (hereinafter abbreviated as a refrigerant). In the rotary compressor 1, the compression mechanism 30 is disposed below the drive mechanism 20 in the sealed casing 10. In addition, lubricating oil 50 supplied to each sliding portion of the compression mechanism 30 is stored in the lower portion of the hermetic casing 10.

  The hermetic casing 10 includes a body 11, a top 12, and a bottom 13. The trunk | drum 11 is a substantially cylindrical member extended in the up-down direction, The upper and lower ends are opening. Further, two connection ports 11a and 11b (see FIG. 5) for introducing inlet tubes 60a and 60b, which will be described later, into the sealed casing 10 are formed on the side surface of the body 11 along the vertical direction. The cylindrical joint pipes 14a and 14b holding the inlet tubes 60a and 60b are joined to the inner peripheral surfaces of the connection ports 11a and 11b by brazing, respectively. In addition, a discharge pipe 15 for discharging the compressed high-temperature and high-pressure refrigerant out of the sealed casing is provided on the upper portion of the body 11. The top 12 is a member that closes the opening at the upper end of the body 11. The top 12 is provided with a terminal terminal 16 connected to the motor 21 of the drive mechanism 20. The bottom 13 is a member that closes the opening at the lower end of the body 11. The sealed casing 10 is formed with a sealed space surrounded by the body 11, the top 12, and the bottom 13.

  The drive mechanism 20 is provided to drive the compression mechanism 30 and includes a motor 21 serving as a drive source and a shaft 22 attached to the motor 21.

  The motor 21 includes a rotor 21a and a stator 21b disposed on the radially outer side of the rotor 21a via an air gap. A shaft 22 is rotatably attached to the rotor 21a. And the rotor 21a has the rotor main body which consists of a laminated | stacked electromagnetic steel plate, and the magnet embed | buried under this rotor main body. The stator 21b has a stator main body made of iron and a coil wound around the stator main body. The motor 21 rotates the rotor 21 a together with the shaft 22 by electromagnetic force generated in the stator 21 b by passing an electric current through the coil.

  The shaft 22 rotates together with the rotor 21a described above, thereby rotating the pistons 34 and 37 of the compression mechanism 30. The shaft 22 is provided with an eccentric portion 22a so as to be positioned in a cylinder chamber S1 of a front cylinder 33 described later, and is provided with an eccentric portion 22b so as to be positioned in a cylinder chamber S2 of the rear cylinder 36. . Pistons 34 and 37 are attached to the eccentric parts 22a and 22b, respectively, and the piston 34 attached to the eccentric part 22a rotates in the cylinder chamber S1 as the shaft 22 rotates, and the eccentric part 22b. The piston 37 mounted on the cylinder rotates in the cylinder chamber S2. The eccentric portion 22a and the eccentric portion 22b are disposed at positions shifted by 180 ° in the rotation direction of the shaft 22.

  The compression mechanism 30 is provided to compress the refrigerant that has passed through the suction pipe assembly 40. The refrigerant compressed by the compression mechanism 30 passes through the air gap between the stator 21b of the drive mechanism 20 and the rotor 21a, cools the drive mechanism 20, and is then discharged from the discharge pipe 15. The compression mechanism 30 includes a front muffler 31, a front head 32, a front cylinder 33, a piston 34, and a double structure from the top to the bottom along the rotation axis of the shaft 22 of the drive mechanism 20. A middle plate 35, a rear cylinder 36 and a piston 37, a rear head 38, and a rear muffler 39 are provided.

  The front muffler 31 includes a first-stage muffler 31 a and a second-stage muffler 31 b, and both are attached to the upper surface of the front head 32. The first-stage muffler 31a forms a muffler space A1 together with the upper surface of the front head 32, and the second-stage muffler 31b forms a muffler space A2 together with the upper surface of the first-stage muffler 31a. And a refrigerant | coolant passes through these two muffler space A1 and A2, and reduction of the noise accompanying discharge of a refrigerant | coolant is achieved.

  The front head 32 is disposed on the upper side of the front cylinder 33 and closes the opening above the cylinder chamber S <b> 1 of the front cylinder 33. As shown in FIG. 2, the front head 32 includes a disc-shaped main body portion 32b having a bearing hole 32a into which the shaft 22 is inserted, and an annular shape protruding upward from the main body portion 32b so as to surround the bearing hole 32a. Boss portion 32c. The main body portion 32b is formed with a concave valve storage chamber 32d and a discharge port 32e for communicating the valve storage chamber 32d and the cylinder chamber S1. A discharge valve 32f for opening and closing the outlet of the discharge port 32e is provided in the valve storage chamber 32d. The main body 32b is formed with a recess 32h having an introduction port 32g for introducing the refrigerant compressed in a cylinder chamber S2 of the rear cylinder 36 described later into the muffler space A1.

  As shown in FIG. 3, the front cylinder 33 is provided with a cylinder chamber S1 at the center portion, and is provided with a bush holding hole 33a, an oil supply hole 33b, and a suction passage 33c outside the cylinder chamber S1. A piston 34 that eccentrically rotates as the shaft 22 rotates is disposed in the cylinder chamber S1. The cylinder chamber S1 communicates with the muffler space A1 through the discharge port 32e. Therefore, the refrigerant compressed by the eccentric rotational movement of the piston 34 attached to the eccentric portion 22a of the shaft 22 is guided from the cylinder chamber S1 to the muffler space A1 through the discharge port 32e. A pair of bushes 34c are provided in the bush holding hole 33a with the blade 34b of the piston 34 interposed therebetween. The pair of bushes 34c has a shape obtained by dividing a columnar member into two vertically. The oil supply hole 33b is provided for supplying the lubricating oil 50 to the piston 34 and the cylinder chamber S1. Specifically, the lubricating oil 50 stored in the lower portion of the sealed casing 10 is sucked up by the pressure difference and supplied to the sliding portion of the piston 34 and the cylinder chamber S1 through the oil supply hole 33b. The suction passage 33c penetrates along the radial direction so as to communicate with the cylinder chamber S1. In this embodiment, as shown in FIG. 4, the suction passage 33c includes a large-diameter passage 33d (inner diameter: r1) into which one end 61a (see FIG. 6) of an inlet tube 60a described later is inserted, and A small-diameter passage 33e (inner diameter: r2) having an inner diameter smaller than that of the large-diameter passage 33d.

  The piston 34 performs eccentric rotational movement along the inner peripheral surface of the cylinder chamber S1, and compresses the refrigerant sucked into the cylinder chamber S1 through the suction passage 33c. As shown in FIG. 3, the piston 34 has an annular roller 34a and a flat blade 34b extending from the outer peripheral surface of the roller 34a. The blade 34b is divided into a suction chamber (low pressure chamber) LR for sucking refrigerant and a discharge chamber (high pressure chamber) HR for discharging compressed refrigerant.

  The middle plate 35 is disposed between the front cylinder 33 and the rear cylinder 36. The middle plate 35 closes the opening below the cylinder chamber S1 of the front cylinder 33 and closes the opening above the cylinder chamber S2 of the rear cylinder 36.

  The rear cylinder 36, the piston 37, the rear head 38, and the rear muffler 39 are the same as the front cylinder 33, the piston 34, the front head 32, and the front muffler 31, respectively, in view of their functions. The refrigerant compressed in the cylinder chamber S2 of the rear cylinder 36 passes through a muffler space (not shown) formed by the rear head 38 and the rear muffler 39, and then the rear head 38, the rear cylinder 36, the middle plate 35, and the front It is introduced into the muffler space A1 through a communication hole (not shown) communicating with the cylinder 33 and the introduction port 32g (see FIG. 2) of the front head 32 described above.

  The suction pipe assembly 40 is provided to supply refrigerant from the outside of the sealed casing 10 to each of the cylinder chamber S1 of the front cylinder 33 and the cylinder chamber S2 of the rear cylinder 36 disposed therein. As shown in FIG. 1, the suction pipe assembly 40 includes an inlet pipe 41 extending in a vertical direction, two branch pipes 42a and 42b bent in a substantially L shape, an inlet pipe 41 and two branch pipes 42a, And a joint member 43 for connecting 42b. Thereby, the refrigerant flowing in from the inlet pipe 41 is divided into two hands in the joint member 43, and then passes through the branch pipes 42a and 42b and is supplied to the cylinder chambers S1 and S2.

  Then, as shown in FIG. 5, substantially cylindrical inlet tubes 60a and 60b are connected to the respective distal ends of the branch pipes 42a and 42b. The inlet tubes 60a and 60b are connected to the suction passages 33c and 36c of the cylinders 33 and 36 in the same direction via joint pipes 14a and 14b joined to the sealed casing 10, respectively. As shown in FIG. 6, the inlet tube 60a has one end 61a connected to the large diameter passage 33d of the suction passage 33c of the front cylinder 33 and the other end 62a connected to the branch pipe 42a. The one end 61a is inserted into the large-diameter passage 33d of the suction passage 33c, and the branch pipe 42a is inserted into the other end 62a, whereby the branch pipe 42a and the suction passage 33c are connected via the inlet tube 60a. Communicate.

And the outer peripheral surface of the other end 62a of the inlet tube 60a and the inner peripheral surface of the joint pipe 14a are joined by brazing. When a CO ₂ refrigerant is used as in the present embodiment, the inside of the sealed casing 10 has a high pressure, and thus it is necessary to strictly manage each gap so that the CO ₂ refrigerant does not leak. Therefore, the gap between the outer peripheral surface of the other end 62a of the inlet tube 60a and the inner peripheral surface of the joint pipe 14a is very small, and the outer peripheral surface of the other end 62a of the inlet tube 60a It is necessary to secure a brazing distance with the inner peripheral surface of the joint pipe 14a by a predetermined length or more.

  In the present embodiment, as shown in FIG. 6, the inner diameter r3 of the one end 61a is smaller than the inner diameter r4 of the other end 62a. In this way, by making the inner diameter r4 of the other end 62a larger than the inner diameter r3 of the one end 61a, the inner diameter of the branch pipe 42a inserted into the other end 62a and the inner diameter r3 of the one end 61a are substantially reduced. It becomes possible to make it the same, and it can pass smoothly, without disturbing the refrigerant | coolant flow between the branch pipe 42a and the inlet tube 60a.

  Further, in the present embodiment, the outer diameter R1 of the one end 61a is smaller than the outer diameter R2 of the other end 62a so that the side inserted into the suction passage 33c of the front cylinder 33 is tapered, and the one end 61a The tip 63a is tapered.

  Here, in this embodiment, the groove part 64a is formed in the outer peripheral surface of the one end 61a of the inlet tube 60a along the circumferential direction, and the annular part O shown in FIG. A ring 70a is attached. The O-ring 70a has a function of sealing between the outer peripheral surface of one end 61a of the inlet tube 60a and the inner peripheral surface of the large-diameter passage 33d of the suction passage 33c, and refrigerant leaks from the portion. I try not to put it out. The O-ring 70a is made of hydrogen nitrile rubber having oil resistance and heat resistance.

  The branch pipe 42b, the inlet tube 60b connected to the branch pipe 42b, and the O-ring 70b attached to the groove portion 64b formed in the inlet tube 60b are respectively the above-described branch pipe 42a and inlet tube in view of their functions. Since it is the same as 60a and O-ring 70a, its description is omitted.

[Features of the rotary compressor of the present embodiment]
The rotary compressor 1 of this embodiment has the following characteristics.

In the rotary compressor 1 of the present embodiment, the grooves 64a and 64b for mounting the O-rings 70a and 70b are formed in the inlet tubes 60a and 60b, respectively, so that it is not necessary to form a groove in the cylinder. It can prevent that the rigidity of 33 and 36 falls. In particular, in the case of a compressor using a CO ₂ refrigerant as in this embodiment, the inside of the sealed casing 10 becomes high pressure, the pressure applied to the cylinders 33 and 36 increases, and distortion appears significantly. It is very effective to prevent the rigidity of 36 from being lowered. In this manner, the distortion of the cylinders 33 and 36 can be suppressed while the inner peripheral surfaces of the suction passages 33c and 36c and the outer peripheral surfaces of the inlet tubes 60a and 60b are kept airtight by the O-rings 70a and 70b.

  In the rotary compressor 1 of the present embodiment, the grooves 64a and 64b are formed on the outer peripheral surfaces of the inlet tubes 60a and 60b. The grooves 64a and 64b are formed on the inner peripheral surfaces of the suction passages 33c and 36c of the cylinders 33 and 36. Therefore, it is possible to suppress an increase in processing cost and to prevent the processing from becoming complicated.

  Moreover, in the rotary compressor 1 of this embodiment, since the groove parts 64a and 64b are formed in the outer peripheral surface of the inlet tubes 60a and 60b, compared with the case where a groove part is formed in the inner peripheral surface of the suction passage of a cylinder, it is a groove part. Cleaning of 64a and 64b can be performed easily. Thereby, the rotary compressor excellent in maintainability can be obtained.

  Further, in the rotary compressor 1 of the present embodiment, the inlet tubes 60a and 60b are respectively connected to the cylinder 33 and the O-rings 70a and 70b in the grooves 64a and 64b formed on the outer peripheral surfaces of the inlet tubes 60a and 60b. It can be connected to 36 suction passages 33c and 36c. For this reason, the O-rings 70a and 70b can be prevented from being damaged by the inlet tubes 60a and 60b.

  Moreover, in the rotary compressor 1 of this embodiment, the high temperature oil supplied to each sliding part of the compressor 1 by using O-rings 70a and 70b made of hydrogenated nitrile rubber having oil resistance and heat resistance. Even under the influence of the presence of compressed high-temperature refrigerant, it is possible to suppress the deterioration of the O-rings 70a and 70b. Thereby, the rotary compressor excellent in maintainability can be obtained.

  Moreover, in the rotary compressor 1 of this embodiment, since the groove parts 64a and 64b are easy to process, it is possible to form the groove parts 64a and 64b at desired locations, and thus the joint pipes 14a and 14b and the inlet tube 60a. And it becomes possible to form the groove parts 64a and 64b in the location away from the joining location which concerns on brazing with 60b. Thereby, the heat due to the brazing becomes difficult to reach the O-rings 70a and 70b, so that the O-rings 70a and 70b can be prevented from being deformed by the heat.

  Moreover, in the rotary compressor 1 of this embodiment, the one end 61a is connected by making the outer diameter R1 of the one end 61a of the inlet tube 60a connected to the suction passage 33c smaller than the outer diameter R2 of the other end 62a. It is possible to reduce the inner diameter r1 of the large diameter passage 33d of the suction passage 33c. As a result, it is possible to prevent the rigidity of the front cylinder 33 from being reduced due to the formation of the large diameter passage 33d. Similarly, a decrease in the rigidity of the rear cylinder 36 can be suppressed.

  Further, in the rotary compressor 1 of the present embodiment, by setting the inner diameter r1 of the large diameter passage 33d to be larger than the inner diameter r2 of the small diameter passage 33e, one end 61a of the inlet tube 60a inserted into the large diameter passage 33d. Can be made substantially the same, and the refrigerant flow between the inlet tube 60a and the suction passage 33c can be smoothly passed without being disturbed. Similarly, the refrigerant flow between the inlet tube 60b and the suction passage 36c can be smoothly passed without being disturbed.

  Further, in the rotary compressor 1 of the present embodiment, the one end 61a of the inlet tube 60a can be easily inserted into the suction passage 33c by making the tip of the one end of the inlet tube 60a tapered, and the groove portion The O-ring 70a can be easily attached to 64a. Similarly, the one end 61b of the inlet tube 60b can be easily inserted into the suction passage 36c, and the O-ring 70b can be easily attached to the groove 64b.

  As mentioned above, although embodiment of this invention was described based on drawing, it should be thought that a specific structure is not limited to these embodiment. The scope of the present invention is shown not only by the above description of the embodiments but also by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

  For example, in the above-described embodiment, an example in which the present invention is applied to a two-cylinder rotary compressor has been described. However, the present invention is not limited to this, and a single-cylinder rotary compressor also includes three or more cylinders. The present invention is also applicable to a machine.

  In the above-described embodiment, the rotary compressor in which the piston and the blade are integrally formed has been described. However, the present invention is not limited to this, and the present invention is also applied to a rotary compressor in which the piston and the blade are separated. Can be applied.

In the above embodiment, the rotary compressor using the CO ₂ refrigerant has been described. However, the present invention is not limited to this, and the present invention can also be applied to a rotary compressor using other than the CO ₂ refrigerant.

  In the above embodiment, an example in which an O-ring made of hydrogen nitrile rubber is used has been described. However, the present invention is not limited to this, and a material excellent in heat resistance and oil resistance can be appropriately selected.

  If the present invention is used, the distortion of the cylinder can be suppressed while the inner peripheral surface of the suction passage and the outer peripheral surface of the inlet tube are kept airtight.

It is sectional drawing which showed the internal structure of the 2 cylinder type rotary compressor which concerns on one Embodiment of this invention. It is the top view which showed the front head of the rotary compressor shown in FIG. It is the top view which showed the front cylinder and piston of the rotary compressor shown in FIG. It is sectional drawing along the AA line of FIG. It is sectional drawing which showed the connection structure of the branch pipe of the suction pipe assembly of the rotary compressor shown in FIG. 1, an inlet tube, and a cylinder. It is sectional drawing which showed the inlet tube of the rotary compressor shown in FIG. It is the (a) top view and (b) front view which showed the O-ring of the rotary compressor shown in FIG.

Explanation of symbols

1 CO ₂ refrigerant rotary compressor 10 Sealed casing 14a, 14b Joint pipe 33 Front cylinder (first cylinder)
33c Suction passage (first suction passage)
36 Rear cylinder (second cylinder)
36c Suction passage (second suction passage)
40 Suction pipe assembly 42a Branch pipe (suction pipe, first branch pipe)
42b Branch pipe (suction pipe, second branch pipe)
60a Inlet tube (first inlet tube)
60b Inlet tube (second inlet tube)
61a One end 62a The other end 63a Tip part 64a Groove part (1st groove part)
64b Groove (second groove)
70a O-ring (seal member, first seal member)
70b O-ring (seal member, second seal member)
S1 Cylinder chamber (first cylinder chamber)
S2 Cylinder chamber (second cylinder chamber)

Claims (7)

A sealed casing;
A cylinder housed in the hermetic casing and having a cylinder chamber and a suction passage communicating with the cylinder chamber;
A suction pipe for supplying refrigerant to the cylinder chamber from the outside of the sealed casing;
An inlet tube having one end connected to the suction passage, the other end connected to the suction pipe, and a groove formed along the circumferential direction on the outer peripheral surface of the one end;
A rotary equipped with a ring-shaped sealing member that is mounted in a groove portion of the inlet tube and seals between an outer peripheral surface of one end of the inlet tube and an inner peripheral surface of the suction passage of the cylinder. Compressor.   The rotary compressor according to claim 1, wherein the seal member is hydrogenated nitrile rubber.   A joint pipe that holds the inlet tube is fixed to the hermetic casing, and an inner peripheral surface of the joint pipe and an outer peripheral surface of the other end of the inlet tube are joined by brazing. The rotary compressor according to claim 1 or 2.   The rotary compressor according to any one of claims 1 to 3, wherein an outer diameter of one end of the inlet tube is smaller than an outer diameter of the other end of the inlet tube.   The suction passage of the cylinder has a large-diameter passage into which one end of the inlet tube is inserted, and a small-diameter passage having a smaller inner diameter than the large-diameter passage. The rotary compressor according to any one of the above.   The rotary compressor according to any one of claims 1 to 5, wherein a tip portion of one end of the inlet tube has a tapered shape. A sealed casing;
A first cylinder housed in the hermetic casing and having a first cylinder chamber and a first suction passage communicating with the first cylinder chamber;
A second cylinder housed inside the hermetic casing and having a second cylinder chamber and a second suction passage communicating with the second cylinder chamber;
Suction having a first branch pipe for supplying refrigerant to the first cylinder chamber from the outside of the sealed casing and a second branch pipe for supplying refrigerant to the second cylinder chamber from the outside of the sealed casing Pipe assemblies,
A first inlet tube having one end connected to the first suction passage, the other end connected to the first branch pipe, and a first groove formed along the circumferential direction on the outer peripheral surface of the one end. When,
A second inlet tube having one end connected to the second suction passage, the other end connected to the second branch pipe, and a second groove formed along the circumferential direction on the outer peripheral surface of the one end. When,
An annular first member that is mounted in the first groove portion of the first inlet tube and seals between the outer peripheral surface of one end of the first inlet tube and the inner peripheral surface of the first suction passage of the first cylinder. A sealing member;
An annular second member that is mounted in the second groove of the second inlet tube and seals between the outer peripheral surface of one end of the second inlet tube and the inner peripheral surface of the second suction passage of the second cylinder. A rotary compressor comprising a sealing member.

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