JP2009062929A - Rotary compressor and refrigerating cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary compressor and a refrigerating cycle device capable of improving reliability. <P>SOLUTION: A compression mechanism part 110 arranged in the rotary compressor 100 of the refrigerating cycle device 1 has a first cylinder 114 forming a first cylinder chamber 114a vertically arranged via a partition plate 113, a second cylinder 115 forming a second cylinder chamber 115a, a first vane 120 arranged in a first vane chamber 119 of the first cylinder 114, a second vane arranged in a second vane chamber of the second cylinder 115, and rollers 153 and 154 arranged in the first and second cylinders 114 and 115. A height clearance between the second cylinder 115 and the roller 154 is set larger than a height difference (a clearance) between the first cylinder 114 and the roller 153 when assembling the compressor 100. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a rotary compressor and a refrigeration cycle apparatus used for an air conditioner and the like, and more particularly to a technique capable of improving reliability.

  In a refrigeration cycle apparatus such as an air conditioner, for example, a rotary compressor in which two compression mechanisms are accommodated with a partition plate in a sealed container is used. As such a rotary compressor, a compressor in which a refrigerant suction passage is provided independently in a cylinder of each compression mechanism section is known (see, for example, Patent Document 1). However, when the suction passage is provided independently for each cylinder, the cross-sectional area of the suction passage becomes smaller as the cylinder thickness decreases. For this reason, the pressure loss due to the suction resistance increases, and the compression efficiency may decrease.

For this reason, it is also known that a common suction passage is provided in the partition plate, and the refrigerant is sucked into the cylinder chamber of each compression mechanism section by branching the suction passage (see, for example, Patent Documents 2 and 3).
JP-A-10-259787 JP 09-250477 A JP 2003-161278 A

  The above rotary compressor has the following problems. That is, when liquid refrigerant is mixed into the refrigerant sucked into the cylinder chamber, more liquid refrigerant is easily sucked into the compression mechanism portion provided on the lower side than the compression mechanism portion provided on the upper side. For this reason, the lower compression mechanism part compresses the liquid refrigerant, and there is a possibility that durability may be reduced or wear resistance may be reduced. For this reason, there exists a possibility that the reliability of a rotary compressor, especially the lower compression mechanism part may be impaired.

  Therefore, the present invention provides a rotary compressor and a refrigeration cycle apparatus in which a suction passage is provided in a partition plate, which has high durability and wear resistance and can improve reliability. It is aimed.

  In order to solve the above problems and achieve the object, the rotary compressor and the refrigeration cycle apparatus of the present invention are configured as follows.

  A sealed container, two eccentric parts, a rotary shaft disposed in the vertical direction in the sealed container, a first cylinder forming a first cylinder chamber, and the eccentric part above the rotary shaft. And a first roller provided in the first cylinder chamber so as to be eccentrically rotatable, a first blade groove formed in the first cylinder, reciprocally slidable in the first blade groove, and A first cylinder that is formed so as to be able to contact the first roller and that bisects the first cylinder chamber, and that forms a second cylinder chamber and a first compression mechanism portion provided in the sealed container. A second roller which is engaged with the eccentric portion on the lower side of the rotating shaft and is provided so as to be eccentrically rotatable in the second cylinder chamber, a second blade groove formed in the second cylinder, and the second blade Reciprocally slidable in the groove, and the second A second compression mechanism portion that is formed so as to be capable of abutting against a roller and includes a second blade that bisects the second cylinder chamber, and is provided in the sealed container and below the first compression mechanism portion; A partition plate provided between the first compression mechanism portion and the second compression mechanism portion and having an insertion hole into which the rotation shaft is inserted, and a partition plate provided in the partition plate and orthogonal to the rotation shaft And a branch passage that is formed from the outer peripheral surface of the partition plate toward the inner peripheral surface side and branches at an angle from the middle of the partition plate above and below the partition plate is formed. A rotary compressor that sucks refrigerant into the first cylinder chamber and the second cylinder chamber through the suction passage, the suction passage communicating with the first cylinder chamber and the second cylinder chamber; Less compression mechanism and partition plate Also provided on one, characterized in that it comprises, and excessive compression preventing means for preventing excessive compression of the second compression mechanism.

  The rotary compressor, a condenser connected to the hermetic rotary compressor, an expansion device connected to the condenser, and an evaporator connected to the expansion device, To do.

  According to the present invention, there is provided a rotary compressor and a refrigeration cycle apparatus in which a suction passage is provided in a partition plate, which has high durability and wear resistance and can improve reliability. Is possible.

  FIG. 1 is an explanatory view showing a configuration of a refrigeration cycle apparatus 1 according to a first embodiment of the present invention and a cross section of a rotary compressor 100 incorporated in the refrigeration cycle apparatus 1, and FIG. 1 is a cross-sectional view showing a partition plate 113 used for 100. FIG.

  As shown in FIG. 1, the refrigeration cycle apparatus 1 is connected to a rotary compressor (hereinafter “compressor”) 100, a condenser 200 connected to a discharge port 101 of the compressor 100, and the condenser 200. The apparatus includes an expansion device 300, an evaporator 400 connected to the expansion device 300, and an accumulator 131 connected to the evaporator 400, and the accumulator 131 is connected to the compressor 100.

  The compressor 100 is a two-cylinder rotary compressor, and includes a hermetic container 102, a compression mechanism part 110 provided at the lower part of the hermetic container 102, an electric motor part 140 provided at the upper part of the hermetic container 102, A rotation shaft 150 that connects the compression mechanism unit 110 and the electric motor unit 140 is provided. The compressor 100 also includes an upper lid 102a for sealing the sealed container 102.

  Further, in the compressor 100, polyol ester oil or ether-based oil is used as lubricating oil (refrigerating machine oil) in the inside, particularly a sliding part such as a compression mechanism part. Depending on the refrigerant used, mineral oil, alkylbenzene, PAG, or fluorinated oil may be used.

  The compression mechanism unit 110 includes a first compression mechanism unit 111 provided below the rotation shaft 150, a second compression mechanism unit 112 provided below the first compression mechanism unit 111, and the first compression mechanism unit 111. And a partition plate 113 provided between the second compression mechanism portion 112 and the second compression mechanism portion 112. In addition, the 1st compression mechanism part 111 and the 2nd compression mechanism part 112 are formed with each component which compresses a refrigerant | coolant in the 1st, 2nd cylinders 114 and 115 mentioned later.

  That is, the compression mechanism unit 110 forms a first cylinder 114 that forms a first cylinder chamber 114a and a second cylinder chamber 115a that are disposed below and above the rotating shaft 150 via a partition plate 113. 2 cylinders 115. The first and second cylinders 114 and 115 are set to have different outer shape dimensions and the same inner diameter dimension. The outer dimension of the first cylinder 114 is formed slightly larger than the inner diameter dimension of the sealed container 102, is press-fitted into the inner peripheral surface of the sealed container 102, and is positioned and fixed by welding from the outside of the sealed container 102.

  A main bearing 116 is superimposed on the upper surface of the first cylinder 114, and a first valve cover 117 is provided so as to cover the main bearing 116. The main bearing 116 has a discharge hole 118 for guiding the refrigerant to the first valve cover 117. Further, the first cylinder 114 is provided with a first vane chamber (first blade chamber) 119 communicating with the first cylinder chamber 114a. In the first vane chamber 119, a first vane (first blade) 120 is accommodated so as to protrude and retract with respect to the first cylinder chamber 114a.

  A sub bearing 121 is superimposed on the lower surface of the second cylinder 115, and a second valve cover 122 is provided so as to cover the sub bearing 121. The second cylinder 115 is formed with a suction passage 123 for sucking refrigerant. The second cylinder 115 is provided with a second vane chamber (second blade chamber) (not shown) communicating with the second cylinder chamber 115a. In this second vane chamber, a second vane (second blade) (not shown) is accommodated so as to protrude and retract with respect to the second cylinder chamber 115a. The leading edges of the first vane 120 and the second vane are formed in a semicircular shape in plan view.

  The first valve cover 117, the main bearing 116, the first cylinder 114, the partition plate 113, the second cylinder 115, the auxiliary bearing 121 and the second valve cover 122 are engaged by a mounting bolt 124, and the first cylinder 114 is interposed therebetween. To be fixed to the sealed container 102.

  The first vane chamber 119 and the second vane chamber are integrally connected to each vane storage groove (not shown) in which both side surfaces of the first vane 120 and the second vane are slidably movable and to each vane storage groove end. Each vertical hole part (not shown) in which the rear-end part of the 1st vane 120 and the 2nd vane is accommodated is provided.

  The first cylinder 114 is provided with a lateral hole that communicates the outer peripheral surface of the first cylinder 114 and the first vane chamber 119 and accommodates the spring member 125. Similarly, the second cylinder 115 is provided with a lateral hole that communicates the outer peripheral surface of the second cylinder 115 and the second vane chamber, and houses a spring member (not shown). These spring members 125 are interposed between the back side end surfaces of the first vane 120 and the second vane and the inner peripheral surface of the sealed container 102, and can apply an elastic force (back pressure) to the first vane 120 and the second vane. It is a compression spring formed.

  As shown in FIG. 2, the partition plate 113 has an insertion hole 113a into which the rotating shaft 150 is inserted, and is formed in a donut shape (disc shape). The upper and lower main surfaces of the partition plate 113 form a part of the first cylinder chamber 114a of the first cylinder 114 and the second cylinder chamber 115a of the second cylinder 115, and eccentric rollers 153 and 154 described later slide. It is formed to be movable. The partition plate 113 has a suction passage 126 formed at a constant distance in the inner circumferential direction from a part of its outer diameter. The suction passage 126 communicates with the upper and lower main surfaces of the partition plate 113. Branch passages 128 and 128 are provided. The partition plate 113 includes a tapered pipe 129 provided in the suction passage 126 and a guide pipe 130 connected to the tapered pipe 129.

  For example, the upper branch passage 127 has an angle θ1 with the outer peripheral surface side as a fulcrum of 45 degrees, the diameter φ1 is 8 mm, and the lower branch passage 128 has an angle θ2 with respect to the suction passage 126. At 45 degrees, the diameter φ2 is 8 mm. Note that the angles θ1 and θ2 of the branch passages 127 and 128 are perpendicular to the rotation shaft 150, and indicate the angles in the vertical direction around the point where the branch passages 127 and 128 intersect the suction passage 126. Yes. The upper branch passage 127 communicates with a suction passage of the first cylinder (not shown), and the lower branch passage 128 communicates with the suction passage 123 of the second cylinder 115.

  A discharge port 101 is connected to the upper end of the sealed container 102. A suction pipe 132 is connected to the bottom of the accumulator 131. The suction pipe 132 communicates directly with the suction passage 126 of the partition plate 113 via the guide pipe 130 and the taper pipe 129.

  The electric motor unit 140 includes a stator 141 that is fixed to the inner surface of the hermetic container 102, and a rotor 142 that is disposed inside the stator 141 at a predetermined interval and into which the rotating shaft 150 is inserted. I have. For example, a brushless DC synchronous motor is used for the electric motor unit 140. The electric motor unit 140 may be an AC motor instead of a brushless DC synchronous motor.

  The rotary shaft 150 is pivotally supported by the main bearing 116 and the auxiliary bearing 121 so that the midway portion and the lower end portion thereof are rotatable. Further, the rotating shaft 150 penetrates through the first and second cylinders 114 and 115 and integrally includes two eccentric portions 151 and 152 formed with a phase difference of about 180 °. The centers of rotation of the eccentric portions 151 and 152 are provided on the same straight line, and are assembled so as to be positioned at the inner diameter portions of the first and second cylinders 114 and 115, respectively. Rollers 153 and 154 that are collinear with each other are accommodated on the circumferential surfaces of the eccentric portions 151 and 152, respectively, so as to be eccentrically rotatable.

  The heights of the rollers 153 and 154 are formed to be substantially the same as the heights of the first and second cylinder chambers 114a and 115a. Accordingly, the rollers 153 and 154 have a phase difference of approximately 180 ° from each other, but the cylinder chambers are set to the same excluded volume by rotating eccentrically in the first and second cylinder chambers 114a and 115a.

  When the rollers 153 and 154 rotate eccentrically along the inner peripheral walls of the first and second cylinder chambers 114a and 115a, the vanes 120 reciprocate along the vane receiving grooves, and the rear end portions of the vanes 120 Are formed so as to freely advance and retract from the respective vertical hole portions.

  In addition, the 2nd compression mechanism part 112 is formed with the following structure as an overcompression prevention means.

  That is, the clearance of the sliding portion of the second compression mechanism portion 112 is set larger than the clearance of the sliding portion of the first compression mechanism portion 111 as an over-compression preventing means. For example, when the height difference (clearance) between the first cylinder 114 and the roller 153 when the compressor 100 (or the compression mechanism unit 110) is assembled is used as a reference, the height between the second cylinder 115 and the roller 154 For example, the clearance X is set to +3 μm. Further, when the height difference (clearance) between the first cylinder 114 and the first vane 120 is used as a reference, the height clearance Y between the second cylinder 115 and the second vane is set to, for example, +3 μm.

  As for these clearances, both the clearance X and the clearance Y may be set to +3 μm with respect to the clearance of the first compression mechanism portion 111, or either the clearance X or Y may be set to +3 μm. The clearances X and Y are +3 μm with respect to the clearance of the first compression mechanism, but are not limited to 3 μm. Furthermore, the clearance between the outer peripheral surface of the roller 154 and the inner peripheral surface of the second cylinder chamber 115a is not limited to the above clearance, and may be larger than the clearance of the first compression mechanism portion. These clearances are clearances when the compressor 100 or the compression mechanism 110 is assembled, and take into account the dimensional tolerance of each component.

  In the refrigeration cycle apparatus 1 configured as described above, full capacity operation is performed in the first compression mechanism unit 111 and the second compression mechanism unit 112 as normal operation. First, by supplying external energy (for example, commercial power supply) to the motor unit 140 of the compressor 100, the rotor 142 rotates, and the rotating shaft 150 fixed to the rotor 142 rotates. At this time, the rotating shaft 150 rotates, but the eccentric portions 151 and 152 rotate eccentrically. Thus, the rotating shaft 150 is rotationally driven, and the eccentric rollers 153 and 154 rotate eccentrically in the first and second cylinder chambers 114a and 115a.

  In the first compression mechanism 111 and the second compression mechanism 112, the first vane 120 and the second vane are always elastically pressed and biased by the spring member 125, and the leading edges of the first vane 120 and the second vane Are in sliding contact with the peripheral walls of the eccentric rollers 153 and 154. By this sliding contact, the inside of the first cylinder chamber 114a and the second cylinder chamber 115a are divided into a suction chamber and a compression chamber.

  The first cylinder chamber 114a has the maximum space capacity when the inner circumferential surface rolling contact position of the first cylinder chamber 114a of the roller 153 coincides with the position of the storage groove of the first vane 120, and the first vane 120 is most retracted. Become. The refrigerant gas is sucked into the first cylinder chamber 114a from the accumulator 131 through the suction pipe 132, the suction passage 126 of the partition plate 113, and the upper branch pipe 127, and fills the first cylinder chamber 114a.

  Along with the eccentric rotation of the roller 153, the rolling contact position of the roller 153 with respect to the inner peripheral surface of the first cylinder chamber 114a moves, and the volume of the compression chamber partitioned by the first cylinder chamber 114a decreases. That is, the gas previously introduced into the first cylinder chamber 114a is gradually compressed. The rotary shaft 150 is continuously rotated, the capacity of the compression chamber of the first cylinder chamber 114a is further reduced, the refrigerant is compressed, and the discharge valve is opened when the pressure rises to a predetermined pressure.

  The compressed refrigerant is discharged into the sealed container 102 through the valve cover 117 and is filled. And it discharges from the discharge outlet 101 of the airtight container 102 upper part. Also in the second compression mechanism 112, the refrigerant sucked from the lower branch pipe 128 is compressed in the same manner as the first compression mechanism 111. The eccentric parts 151 and 152 of the first compression mechanism part 111 and the second compression mechanism part 112 are formed with a phase difference of about 180 °. For this reason, either the first compression mechanism 111 or the second compression mechanism 112 performs a compression stroke, and the other performs a suction stroke.

  As described above, the refrigerant compressed by the first compression mechanism 111 and the second compression mechanism 112 moves from the discharge hole 118 into the sealed container 102 via the first valve cover 117. The refrigerant sequentially passes through the condenser 200, the expansion device 300, and the evaporator 400 from the discharge port 101 provided in the sealed container 102, and returns to the compressor 100 through the accumulator 131.

  In such a refrigerant compression process, a liquid refrigerant may be mixed in the refrigerant sucked from the accumulator 131. When compressing such a gas-liquid mixed refrigerant, not only gas but also liquid (compression) is compressed. However, since the gas-liquid mixed refrigerant has a lower compression rate than when compressing the gaseous refrigerant, the pressure in the first and second cylinders 114 and 115 (compression chamber) increases when compressed to the same volume. . For this reason, a load is applied to the compression mechanism unit 110, and sliding products such as the eccentric rollers 153 and 154, the main bearing 116, the auxiliary bearing 121, and the first and second vanes 120 may be worn. In particular, the lower branch pipe 128 is easier to enter the liquid refrigerant than the upper branch pipe 127 because of its shape.

  However, the clearance of the sliding portion of the second compression mechanism portion 112 (for example, at least one of the clearances X and Y) is made larger than that of the first compression mechanism portion 111, so that the second compression mechanism portion 112 is compressed during the compression stroke. When a liquid refrigerant is mixed and the pressure in the compression chamber increases, a small amount of the refrigerant escapes to the suction chamber or the second vane chamber. Even if the gas-liquid mixed refrigerant is compressed and the pressure increases during the compression process, a small amount of the refrigerant is released, so that the pressure is reduced and excessive over-compression is prevented, and a high load is applied to the second compression mechanism 112. There is no. For this reason, each wear amount reduces by providing clearance from the 1st compression mechanism part 111 in the 2nd compression mechanism part 112. FIG.

  Next, a comparison of the amount of wear between the second compression mechanism portion 112 according to the present embodiment and the second compression mechanism portion of the conventional clearance (the same clearance as the first compression mechanism portion 111) will be described.

  FIG. 3 is a graph showing the amount of wear at each part of the second compression mechanism 112. In FIG. 3, the left side is the conventional clearance, that is, the wear amount W1 of the second compression mechanism part with the same clearance as the first compression mechanism part 111, and the right side is the second compression mechanism part with the clearance of the present embodiment. A wear amount W2 of 112 is shown.

  An endurance test is performed on the wear amount W1 of the second compression mechanism portion in such a conventional clearance and the wear amount W2 of the second compression mechanism portion 112 of the present embodiment. As conditions for this durability test, R410A is used as the refrigerant, the polyol oil is the lubricating oil, the rotation speed of the compressor 100 is 120 rps, the discharge pressure (gauge pressure) is 3.64 MPag, and the suction pressure (gauge pressure) is 0.7 MPag. It was. Moreover, discharge temperature was 100 degrees C or less, and it performed by 1000 hours continuous operation. All conditions other than the clearances X and Y are the same. Further, the wear amount W2 is a value obtained by averaging the wear amounts of the three conditions when the clearance X is provided, when the clearance Y is provided, and when both the clearances X and Y are provided.

  In FIG. 3, V1 indicates the amount of wear at the vane tip, V2 indicates the amount of wear in the radial direction of the sliding portion of the auxiliary bearing, and V3 indicates the amount of wear of the partition plate.

  As a result of carrying out such an endurance test, as shown in FIG. 3, when the wear amount W1 of the conventional clearance is set to 100, the wear amount W2 of the present embodiment is 98 at the vane tip V1 and the auxiliary bearing. The wear amount is 95, and the wear amount is 95 with the partition plate. That is, the amount of wear decreased.

  Thus, according to the refrigeration cycle apparatus 1 of the present invention, the suction refrigerant is set by setting the clearance of the sliding portion of the second compression mechanism portion 112 to be larger than the clearance of the sliding portion of the first compression mechanism portion 111. When the liquid refrigerant is mixed in and the pressure in the compression chamber increases, a small amount of refrigerant leaks (moves) from the clearance to the suction chamber side. Thereby, overcompression was prevented, and as shown in FIG. 3, it became possible to reduce the wear amount W2 of each site | part V1, V2, V3 to 95-98% compared with the past (100%). In this way, a decrease in capability due to wear of the sliding portion is prevented. Further, it becomes possible to prevent the generation of noise and noise due to the occurrence of gaps between the components due to wear of the sliding portion, and to improve the reliability of the compressor 100 and the refrigeration cycle apparatus 1. Is possible. If the clearance of the sliding portion is increased, the compression efficiency during normal operation may be lowered. However, for example, an increase in the clearance of about 3 μm is within an allowable range.

Next, a refrigeration cycle apparatus 1A according to a second embodiment of the present invention will be described. In addition, detailed description of the same functional part as the refrigeration cycle apparatus 1 according to the first embodiment is omitted.
The refrigeration cycle apparatus 1A has a configuration in which no member other than the second vane is accommodated in the second vane chamber of the second cylinder 115 of the second compression mechanism 112, that is, as the overcompression preventing means, It has the structure which does not have the spring member which presses 2 vanes.

  In addition, a part of the outer shape of the second cylinder 115 is formed in a shape that is exposed in the sealed container 102, and a second vane chamber is provided in a portion exposed to the sealed container 102.

  The clearance of the second compression mechanism 112 is the same as the clearance of the first compression mechanism 111. However, as in the second embodiment, the clearance of the sliding portion of the second compression mechanism portion 112 may be larger than the clearance of the sliding portion of the first compression mechanism portion 111.

  In the refrigeration cycle apparatus 1A configured as described above, the second vane chamber and the second vane rear end portion directly receive the pressure in the case. Further, the tip end portion of the second vane faces the second cylinder chamber 115a, and the tip end portion of the second vane receives the pressure in the second cylinder chamber 115a. As a result, the second vane moves in the direction from the higher pressure to the lower pressure in accordance with the magnitude of the pressure received by the front end and the rear end.

  That is, when the gas-liquid mixed refrigerant or the like is sucked into the second cylinder chamber 115a and compressed, the pressure in the compression chamber of the second cylinder chamber 115a becomes high. When the pressure in the compression chamber becomes higher than the pressure in the sealed container 102, the pressure at the tip of the second vane becomes higher than the back pressure of the second vane by the sealed container 102, so that the vane is separated from the circumferential wall of the eccentric roller 154. Move in the direction you want. For this reason, a part of the high-pressure refrigerant in the compression chamber of the second cylinder chamber 115a moves to the suction chamber, and the pressure in the compression chamber decreases. When the pressure in the compression chamber becomes lower than the pressure in the sealed container 102 in this way, the second vane comes into contact with the peripheral wall of the eccentric roller 154 again.

  As described above, according to the refrigeration cycle apparatus 1A of the present invention, the second vane can be moved by the pressure between the compression chamber of the second cylinder chamber 115a and the closed container 102, so that the liquid refrigerant is mixed into the suction refrigerant. When the pressure in the compression chamber increases, excessive overcompression can be prevented. For this reason, it becomes possible to prevent the damage of the 2nd compression mechanism part 112. FIG.

  In addition, the confirmation test was done as confirmation of these effects. As conditions for the confirmation test, R410A is used as the refrigerant, polyol ester oil is used as the lubricating oil, the compressor 100 is alternately turned ON / OFF, and the rotational speed is varied from 0 rps to 120 rps. The discharge pressure (gauge pressure) was 3.0 MPag, and the suction pressure (gauge pressure) was 0.85 MPag. The discharge temperature is set to 100 ° C. or less, the test time is ON for 3 minutes, and the OFF time is 2 minutes for 150 hours, and the second compression mechanism 112 is checked for damage due to liquid back.

  After the refrigeration cycle apparatus 1 was operated for 150 hours under the above conditions, damage to the second compression mechanism 112 was confirmed, but no damage was seen.

  As described above, according to the refrigeration cycle apparatus 1A according to the present embodiment, the second vane can be moved by the pressure in the compression chamber of the second cylinder chamber 115A and the pressure in the sealed container 102. It is possible to prevent excessive overcompression of the second compression mechanism 112 and prevent damage to the second compression mechanism 112. This also improves the reliability of the refrigeration cycle apparatus 1A.

Next, a refrigeration cycle apparatus 1B according to a third embodiment of the present invention will be described. In addition, detailed description of the same functional parts as the refrigeration cycle apparatuses 1 and 1A is omitted.
The refrigeration cycle apparatus 1B has an angle θ2 of the lower branch passage 128 below the partition plate 113, an angle larger than an angle θ1 of the upper branch passage 127, and a diameter φ2 of the lower branch passage 128 as overcompression preventing means. The upper branch passage 127 is formed to have a diameter smaller than the diameter φ1.

  For example, the angle θ1 of the upper branch passage 127 is 45 degrees, the diameter φ1 is 8 mm, the angle θ2 of the lower branch passage 128 is 60 degrees, and the diameter φ2 is 6 mm. Note that the difference between the angles and diameters (θ1 <θ2, φ2 <φ1) provided in the upper and lower branch passages 127 and 128 may be either the angle or the diameter.

  In the refrigeration cycle apparatus 1B configured as described above, the angle θ2 of the lower branch passage 128 is made larger and the diameter φ2 is made smaller than the upper branch passage 127, so that the passage resistance of the lower branch passage 128 is increased. Will be.

  When the refrigerant is a gas, even if the passage resistance increases somewhat, there is no significant difference in the suction amount. However, in the case of a liquid refrigerant, the passage resistance is increased, so that the suction amount of the liquid refrigerant is reduced. This makes it possible to reduce the amount of liquid refrigerant sucked into the second cylinder chamber 115a, and excessive compression of the compression chamber of the second cylinder chamber 115a during the compression stroke of the second compression mechanism 112. Can be prevented.

  In addition, the confirmation test was done as confirmation of these effects. As conditions for the confirmation test, R410A is used as the refrigerant, polyol ester oil is used as the lubricant, the compressor 100 is turned ON / OFF, and the rotational speed is varied from 0 rps to 120 rps. The discharge pressure (gauge pressure) was 3.0 MPag, and the suction pressure (gauge pressure) was 0.85 MPag. The discharge temperature is set to 100 ° C. or less, the test time is ON for 3 minutes, and the OFF time is 2 minutes for 150 hours, and the second compression mechanism 112 is checked for damage due to liquid back.

  After the refrigeration cycle apparatus 1B was operated for 150 hours under the above conditions, the second compression mechanism 112 was confirmed, but no damage was found.

  As described above, according to the refrigeration cycle apparatus 1B according to the present embodiment, the passage resistance of the lower branch passage 128 is larger than that of the upper branch passage 127, so the liquid that is sucked into the second cylinder chamber 115a. It becomes possible to reduce the suction amount of the refrigerant. As a result, it is possible to prevent excessive overcompression of the second cylinder chamber 115a during the compression stroke of the second compression mechanism 112. Thereby, it is possible to prevent the second compression mechanism 112 from being damaged and improve the reliability of the refrigeration cycle apparatus 1B.

Next, a refrigeration cycle apparatus 1C according to a fourth embodiment of the present invention will be described with reference to FIG. FIG. 4 is an explanatory diagram showing a partial cross section of the second vane 160 used in the refrigeration cycle apparatus 1C according to the fourth embodiment of the present invention. In addition, detailed description of the same functional part as the refrigeration cycle apparatuses 1-1B is omitted.
As shown in FIG. 4, the refrigeration cycle apparatus 1 </ b> C has a second vane 160 in the second compression mechanism unit 112. The second vane 160 includes a vane main body 161 formed of a SKH material that has been processed and polished, and a DLC (Diamond Like Carbon) film 163 having an inclined film 162 for forming a gradient composition formed on the vane main body 161. It has. The DLC film 163 is formed to a thickness of 0.5 to 3 μm. Note that a high-strength surface treatment film may be used without using the DLC film 163. The outer diameter of the second vane 160 is the same as the second vanes of the other refrigeration cycle apparatuses 1 to 1B.

  In FIG. 4, the boundary line of the gradient film 162 is shown in the DLC film 163. This is the DLC film 163 in which the gradient film 162 is provided on the upper surface of the vane body 161, and has a gradient composition. Therefore, it is assumed that there is actually no boundary line.

  In addition, the 1st compression mechanism part 111 and the 2nd compression mechanism part 112 have the structure in any one of the said 1st-3rd embodiment.

  In the refrigeration cycle apparatus 1 configured as described above, the vane body 161 is provided with the DLC film 163 having the gradient film 162 for making the gradient composition, and the DLC film 163 having high adhesion is provided with high wear resistance. Thus, it is possible to prevent a decrease in the coefficient of performance (COP) due to wear.

  In addition, the confirmation test of the presence or absence of the damage by abrasion at the time of using the 2nd vane 160 which has the DLC film 163 mentioned above was done. In this confirmation test, a test under the same conditions as the confirmation test performed in the refrigeration cycle apparatuses 1A and 1B is performed in the refrigeration cycle apparatus 1C of the present embodiment, and detailed description thereof is omitted.

  After the confirmation test, the second compression mechanism 112 was confirmed, but no damage was found. In this way, by providing the DLC film 163 on the second vane 160, the second vane 160 has a strength that can withstand even if the compression chamber of the second cylinder 115 becomes high pressure.

  Next, comparison of coefficient of performance (COP) between the second compression mechanism unit 112 of the refrigeration cycle apparatus 1C and the second compression mechanism unit using the second vane without the conventional DLC film 163 will be described.

  FIG. 5 is a graph showing a coefficient of performance V4 (W4) for the input V5 of the refrigeration cycle apparatus 1C according to the present invention and a coefficient of performance V4 (W3) for the input V5 of the conventional refrigeration cycle apparatus. is there. In FIG. 5, the left side shows the coefficient of performance W3 formed by the conventional clearance, and the right side shows the coefficient of performance W4 of the present embodiment.

  Thus, performance measurement of the coefficient of performance W3 of the refrigeration cycle apparatus having the conventional second vane and the coefficient of performance W4 of the refrigeration cycle apparatus 1C of the present embodiment is performed. As conditions for this performance test, when the rotation speed of the compressor 100 is 60 rps, the discharge pressure is 2542 kPa, the suction pressure is 867 kPa, the pre-expansion valve temperature is 34.3 ° C., the suction temperature is 12.7 ° C., and the condensation temperature is 42. The temperature was 3 ° C, the evaporation temperature was 2.7 ° C, the degree of supercooling was 8 ° C, and the degree of heating was 10 ° C. The coefficient of performance (COP) at this time is measured.

In FIG. 5, V4 indicates the coefficient of performance, and V2 indicates the input.
As a result of performing such a performance test, when the coefficient of performance V4 using the conventional second vane and the input V5 are set to 100, as shown in FIG. 5, the second vane 160 of the present embodiment is used. The coefficient of performance V4 was 102 and the input V5 was 98.

  Thus, the input V5 can be reduced to 98, and the coefficient of performance (COP) V4 can be improved to 102.

  As described above, according to the refrigeration cycle apparatus 1C of the present invention, the DLC film 163 is formed on the surface of the second vane 160, thereby preventing damage and wear even when the gas-liquid mixed refrigerant is compressed. It becomes possible. In this way, it is possible to improve the coefficient of performance, prevent wear, and prevent a decrease in the coefficient of performance due to wear.

  Further, by allowing the inclined film 162 to be continuous between the DLC film 163 and the vane body 161, it is possible to improve adhesion and prevent peeling.

  As described above, according to the refrigeration cycle apparatus 1C according to the present embodiment, the strength of the second vane 160 is increased by the DLC film 163 to prevent damage and wear, thereby improving the coefficient of performance. In addition, it is possible to prevent a decrease in the coefficient of performance.

  The present invention is not limited to the above embodiment. For example, in the above-described example, in the refrigeration cycle apparatuses 1A to 1C, the clearance between the first compression mechanism unit 111 and the second compression mechanism unit 112 is made equal. The clearances X and Y of the two compression mechanism 112 may be used. Similarly, in the refrigeration cycle apparatuses 1, 1 </ b> B, and 1 </ b> C, the second vane may have no spring member as in the refrigeration cycle apparatus 1 </ b> A. That is, the prevention means of the refrigeration cycle apparatuses 1 to 1C are not used, but can be applied as a combination of two or more prevention means. In this way, by combining the refrigeration cycle apparatuses 1 to 1C, it is possible to prevent damage in the second compression mechanism unit 112, and further improve the coefficient of performance. As a result, reliability can be improved.

  In the above-described refrigeration cycle apparatus 1A, the rear surface of the second vane is configured to have nothing, and can be moved by the balance between the compression chamber and the internal pressure of the sealed container 102. However, in order to assist the movement of the second vane. In addition, a magnet that assists the movement of the second vane in the opening direction can be applied. With such a configuration, when the compression chamber of the second cylinder chamber 115a becomes a high pressure, the second vane is reliably moved and the followability is improved. Thereby, durability and abrasion resistance are further improved, and reliability is further improved.

  Furthermore, although the DLC film 163 is provided as the surface treatment film on the second vane 160 of the refrigeration cycle apparatus 1C described above, this may be a high-strength CrN film or TiN film instead of the DLC film 163. Thus, by providing a high-strength film, it is possible to reliably improve the wear resistance. In addition, various modifications can be made without departing from the scope of the present invention.

Explanatory drawing which shows the structure of the refrigerating-cycle apparatus which concerns on the 1st Embodiment of this invention, and the cross section of the rotary compressor integrated in this refrigerating-cycle apparatus. Sectional drawing which shows the partition plate used for the rotary compressor. The graph which shows the amount of wear of each site | part of the 2nd compression mechanism part of the same refrigeration cycle apparatus. Explanatory drawing which shows the partial cross section of the 2nd vane used for the refrigerating-cycle apparatus which concerns on the 4th Embodiment of this invention. The graph which shows the coefficient of performance of the same refrigeration cycle apparatus.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1,1A, 1B, 1C ... Refrigeration cycle apparatus, 100 ... Rotary compressor (compressor), 101 ... Discharge port, 102 ... Sealed container, 102a ... Upper lid, 110 ... Compression mechanism part, 111 ... Compression mechanism part, 112 DESCRIPTION OF SYMBOLS ... Compression mechanism part, 113 ... Partition plate, 113a ... Insertion hole, 114 ... 1st cylinder, 114a ... 1st cylinder chamber, 115 ... 2nd cylinder, 115a ... 2nd cylinder chamber, 116 ... Main bearing, 117 ... Valve cover , 118 ... discharge hole, 119 ... first vane chamber, 120 ... first vane, 121 ... auxiliary bearing, 122 ... valve cover, 123 ... suction passage, 124 ... bolt, 125 ... spring member, 126 ... suction passage, 127 ... Upper branch passage, 128 ... lower branch passage, 129 ... taper pipe, 130 ... guide pipe, 131 ... accumulator, 132 ... suction pipe, 140 ... motor part, 1 1 ... stator, 142 ... rotor, 150 ... rotary shaft, 151, 152 ... eccentric portion, 153, 154 ... roller, 200 ... condenser, 300 ... expansion device, 400 ... evaporator.

Claims (5)

A sealed container;
A rotating shaft having two eccentric parts and arranged in the vertical direction in the sealed container;
A first cylinder that forms a first cylinder chamber, a first roller that is engaged with the eccentric portion on the upper side of the rotation shaft, and that is eccentrically rotatable in the first cylinder chamber, and is formed on the first cylinder. A first blade groove, and a first blade formed so as to be able to reciprocate in the first blade groove and to be in contact with the first roller, and to bisect the first cylinder chamber; A first compression mechanism provided in the interior;
A second cylinder that forms a second cylinder chamber, a second roller that is engaged with the eccentric portion on the lower side of the rotation shaft, and that can be eccentrically rotated in the second cylinder chamber, is formed on the second cylinder. A second blade groove, a second blade formed so as to be capable of reciprocating in the second blade groove and capable of abutting against the second roller, and bisecting the second cylinder chamber. A second compression mechanism provided below the first compression mechanism,
A partition plate provided between the first compression mechanism portion and the second compression mechanism portion and having an insertion hole into which the rotating shaft is inserted;
The partition plate is provided in a direction orthogonal to the rotation axis and from the outer peripheral surface of the partition plate toward the inner peripheral surface, and from the middle part above and below the partition plate, respectively. A branch passage that branches at an angle is formed, and includes a suction passage that communicates with the first cylinder chamber and the second cylinder chamber, and the first cylinder chamber and the second passage through the suction passage. In the rotary compressor that sucks refrigerant into the cylinder chamber,
An over-compression preventing means for preventing over-compression of the second compression mechanism section.   2. The over-compression preventing means is formed by forming a clearance of a sliding portion of the second compression mechanism portion larger than a clearance of a sliding portion of the compression mechanism portion. Rotary compressor.   2. The rotary compressor according to claim 1, wherein the over-compression preventing means is configured such that passage resistance of the lower branch passage is larger than that of the upper branch passage.   2. The rotary compressor according to claim 1, wherein the over-compression preventing means is configured to abut the second blade on the outer peripheral surface of the second roller only by pressure in the sealed container. . A rotary compressor according to any one of claims 1 to 4,
A condenser connected to this hermetic rotary compressor;
An expansion device connected to the condenser;
A refrigeration cycle apparatus comprising an evaporator connected to the expansion device.

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