JP5421732B2 - Hermetic compressor, refrigeration cycle equipment - Google Patents

Description

  The present invention relates to a hermetic compressor and a refrigeration cycle apparatus, and more particularly to a hermetic compressor having an improved discharge hole configuration of a discharge muffler and a refrigeration cycle apparatus using the same.

  Normally, in a hermetic compressor used for refrigerant compression, pulsation of refrigerant gas discharged from the compression chamber of the compression mechanism into the hermetic container is a factor, which causes noise deterioration.

  Therefore, in order to reduce the pressure pulsation of the refrigerant discharged from the compression chamber of the compression mechanism and reduce noise, a discharge muffler is provided, and the refrigerant discharged from the compression chamber is discharged into the sealed container through the discharge muffler. I am doing so. Conventionally, a proposal has been made in which a plurality of discharge holes for discharging the refrigerant in the muffler chamber into a sealed container are provided in the discharge muffler (see, for example, Patent Document 1).

Japanese Patent Laid-Open No. 1-280697

  However, the discharge muffler of the hermetic compressor described in Patent Document 1 cannot sufficiently reduce the noise transmitted to the outside of the hermetic container, and there is a demand for a hermetic compressor in which noise is further reduced. Yes.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to provide a hermetic compressor that can reduce noise transmitted to the outside of the hermetic container.

  Another object of the present invention is to provide a refrigeration cycle apparatus capable of reducing noise.

In order to achieve the above-described object, a hermetic compressor according to the present invention includes an electric motor unit in a hermetic container , a cylinder that is driven by the electric motor unit via a rotating shaft, and forms a cylinder chamber, and the rotating shaft. a roller eccentrically rotating within said cylinder is engaged with the eccentric portion, is attached to the cylinder housing and a compression mechanism that having a bearing for supporting the rotating shaft, of the cylinder chamber to said bearing A discharge port for discharging the refrigerant in the compression chamber, a discharge valve for opening and closing the discharge port, and a longitudinal end of a valve stopper for limiting a lift amount of the discharge valve are fixed to the bearing; and in hermetic compressor discharge muffler forming a muffler chamber covering the discharge valve and the valve stopper is provided attached to the bearing, the refrigerant in the muffler chamber to the discharge muffler of the hermetic container A single discharge port for discharging the provided therebetween, the discharge holes, the longitudinal length of the valve stopper when is L, the fixing portion center of the valve stopper as viewed in the axial direction of the rotary shaft and it is characterized in that it is formed within the center circle and the radius (L / 2).

  A refrigeration cycle apparatus according to the present invention includes the hermetic compressor according to any one of claims 1 to 4, a radiator, an expansion device, and an evaporator.

  According to the hermetic compressor according to the present invention, it is possible to provide a hermetic compressor that can rectify the discharge gas, reduce the pulsation of the fluid, and reduce the noise propagated outside the hermetic container. .

  Moreover, according to the refrigerating cycle apparatus which concerns on this invention, the refrigerating cycle apparatus which can reduce a noise can be provided.

1 is a conceptual diagram of an embodiment of a hermetic compressor according to the present invention and a refrigeration cycle apparatus using the same. The longitudinal cross-sectional view which follows the AO-A 'line of FIG. 3 of the main bearing and discharge muffler used for one Embodiment of the hermetic compressor which concerns on this invention. The top view of the main bearing and discharge muffler which were used for one Embodiment of the hermetic type compressor concerning the present invention and looked at the discharge muffler in the state which can be seen through. 1 is a longitudinal sectional view of a part of a main bearing and a discharge muffler used in an embodiment of a hermetic compressor according to the present invention. The correlation diagram which shows the test result regarding the frequency and the noise level using one Embodiment of the hermetic compressor which concerns on this invention. The correlation diagram which shows the test result regarding the position of a discharge hole and noise level using one Embodiment of the hermetic type compressor which concerns on this invention. The correlation diagram which shows the test result regarding the ratio of the discharge hole area and discharge port area and noise level using one Embodiment of the hermetic compressor which concerns on this invention. The longitudinal cross-sectional view for description of the volume of the muffler chamber used for one Embodiment of the sealed compressor which concerns on this invention, and the volume of the predetermined space in a sealed container. The correlation diagram of the muffler chamber volume used for one embodiment of the hermetic compressor concerning the present invention, the predetermined space volume in a sealed container, and resonance noise. The side view which shows in part the sealing terminal used for one Embodiment of the sealed compressor which concerns on this invention. The longitudinal cross-sectional view which shows the welding work state of the sealing terminal used for one Embodiment of the sealed compressor which concerns on this invention. The figure which expands and shows the A section of FIG. The correlation diagram of the inclination | tilt angle of the end surface of the sealing terminal used for one Embodiment of the sealed compressor which concerns on this invention, and the distortion | strain of a sealing terminal. The figure explaining the vector of the sealing terminal deformation | transformation by the difference in the inclination angle of the end surface of the sealing terminal used for one Embodiment of the sealed compressor which concerns on this invention. The longitudinal cross-sectional view which shows a part of sealed terminal of the 1st modification used for one Embodiment of the sealed compressor which concerns on this invention. The longitudinal cross-sectional view which shows a part of sealed terminal of the 2nd modification used for one Embodiment of the sealed compressor which concerns on this invention.

  An embodiment of a hermetic compressor according to the present invention and a refrigeration cycle apparatus using the same will be described with reference to the accompanying drawings.

  As shown in FIG. 1, the refrigeration cycle apparatus 101 according to the present invention includes a hermetic compressor 1, a radiator 102, an expansion device 103, and an evaporator 104 according to this embodiment. The pipes 105b are connected in a cycle.

  The hermetic compressor 1 includes a hermetic container 2, and includes an electric motor unit 3 accommodated in the hermetic container 2, and a compression mechanism unit 5 coupled to the electric motor unit 3 via a rotating shaft 4. Is attached externally.

The refrigeration cycle apparatus 101 is suitable for use in a heat pump hot water supply apparatus, and carbon dioxide (CO ₂ ) is used as a refrigerant. The CO ₂ refrigerant has a characteristic that the pressure is about 3.5 times higher than that of the R410A refrigerant used in an air conditioner or the like, and the inside of the sealed container 2 becomes high pressure.

  For this reason, the container upper part 2a, the container lower part 2b, and the container main body 2c of the closed container 2 are thicker than the thickness of the closed container of the hermetic compressor using the R410A refrigerant. For example, the container main body 2c uses the R410A refrigerant. While the thickness of the container main body of the hermetic compressor is about 3 mm, it is as thick as 7 to 8 mm.

  The electric motor unit 3 includes a stator 31 that is press-fitted into the hermetic container 2, and a rotor 32 that is rotatably disposed on the inner periphery of the stator 31 and is fixed to the upper end of the rotating shaft 4.

  Electric power is supplied to the motor unit 3 from a sealed terminal 7 provided on the container upper part 2a of the sealed container 2 through a lead wire 8 having a cluster 8a.

  The hermetic compressor 1 is a high-pressure type in a hermetic container that discharges the refrigerant compressed by the compression mechanism unit 5 into the inner space of the hermetic container 2, and the compression mechanism unit 5 is arranged below the electric motor unit 3 and has a rotating shaft. 4 is provided with a cylinder 51 located in the lower part of 4.

  A main bearing 52 is attached and fixed to the upper surface portion of the cylinder 51, and a sub bearing 53 is attached and fixed to the lower surface portion, and a cylinder chamber 54 is formed in a space defined by the cylinder 51, the main bearing 52 and the sub bearing 53. Is formed.

  In the cylinder chamber 54, an eccentric portion 4a provided integrally with the rotary shaft 4 and a roller 55 engaged with the peripheral surface of the eccentric portion 4a are disposed.

  The roller 55 has the same thickness along the circumferential direction, and rotates eccentrically with the eccentric portion 4 a as the rotating shaft 4 rotates.

  A part of the outer peripheral wall along the axial direction of the roller 55 is substantially in contact with the inner peripheral wall of the cylinder 51, and the contact position gradually increases along the circumferential direction of the cylinder 51 with the eccentric rotation of the roller 55. Displace.

  Further, a blade (not shown) is in contact with the outer peripheral wall of the roller 55 along the axial direction.

  One end of the blade is elastically pressed and urged by a spring member (not shown) accommodated in a spring accommodation hole, so that the other end of the blade is in elastic contact with the peripheral surface of the roller 55.

  The blade protrudes into the cylinder chamber 54 and slides in a blade groove (not shown) having one end opened to the cylinder chamber 54 and the other end opened to the back hole (not shown). It is divided into a compression chamber side communicating with a discharge port 52p provided in the main bearing 52 and a suction chamber side communicating with a suction hole (not shown).

  As shown in FIGS. 2 to 4, the main bearing 52 provided with the discharge port 52p is provided with a valve mechanism accommodating recess 52a at a position facing the discharge port 52p, and the valve mechanism accommodating recess 52a includes a discharge mechanism. A discharge valve 52b that opens and closes the port 52p as appropriate and a valve stopper 52c that limits the opening of the discharge valve 52b are fixedly accommodated in the main bearing 52 by a fixing member 52d.

  Further, a discharge muffler 9 having a substantially deep dish shape and having a muffler chamber 9a communicating with the valve mechanism housing recess 52a and a discharge hole 9b is airtightly attached to the main bearing 52.

  FIG. 3 shows the upper surface of the main bearing 52 viewed in a state where the discharge muffler 9 can be seen through.

  The hermetic compressor according to the present invention having the above-described structure is made by specifying the number of discharge holes provided in the discharge muffler and the arrangement position thereof.

  Further, the ratio of the area of the discharge hole of the discharge muffler to the area of the discharge port is specified within a predetermined range.

  Further, the volume ratio between the volume of the muffler chamber and the space volume in the sealed container formed by one end side of the compression mechanism section and one end side of the compression mechanism section on the electric motor section side is removed from an integer multiple of 2 or more. It is made in.

  The specification of the number and position of these discharge holes, the specification of the range of the area ratio, and the removal of the volume ratio from an integer multiple of 2 or more are based on the knowledge obtained from the tests conducted by the inventors described below. It is.

  First, as shown in FIG. 3, the noise level was measured by changing the position of the discharge hole 9b using a hermetic compressor including the discharge muffler 9 provided with one discharge hole 9b. As shown in FIG. Results were obtained. According to this test result, when the length of the valve stopper 52c in the longitudinal direction is L, the position of the discharge hole 9b is within a radius (1/2) L or less with the fixed portion center c of the valve stopper 52c as the center. That is, it has been found that the noise level is greatly reduced within the range of the circle C of (L / 2) from the center of the fixed portion center c of the valve stopper 52c.

  The embodiment of the present invention shown in FIG. 3 in which the position of the discharge hole 9b is provided at a position about (L / 4) from the center of the fixed portion c of the valve stopper 52c within the above range, and two discharge holes are provided. When the relationship between the frequency of the conventional hermetic compressor provided and the noise level was examined, the results shown in FIG. 5 were obtained.

  Assuming that the noise level of each frequency when the discharge muffler is not provided is a reference 0, it has been found that the noise level is lower than the conventional one in a high frequency range of 1000 Hz or higher.

  In the range of 400 to 800 Hz, the noise level is higher than when no discharge muffler is provided, but it is originally a portion where the absolute value of the noise level is low, and there is little effect on the noise.

  Based on such knowledge, as shown in FIGS. 2 and 4, a single discharge hole 9b is provided on the upper surface of the discharge muffler 9, and the discharge hole 9b has a length in the longitudinal direction of the valve stopper 52c. L is formed within a circle C having a radius (L / 2) centered on the center c of the fixed portion of the valve stopper 52c when viewed from the axial direction of the rotary shaft 4.

  The discharge gas compressed to high temperature and high pressure in the compression chamber of the cylinder chamber 54 is discharged from the discharge port 52p to the muffler chamber 9a and further discharged from the discharge hole 9b to the sealed container 2, but the discharge hole 9b has a radius (L The noise transmitted outside the sealed container 2 is reduced by providing it within the range of the circle of / 2). This is because the discharge hole 9b is provided at a position some distance away from the discharge port 52p, and the residence time of the discharge gas discharged to the hermetic container 2 in the muffler chamber 9a becomes longer, thereby rectifying the discharge gas. It is assumed that a part of the factor is that the pulsation of the fluid is reduced.

Further, when the area of the discharge hole 9b is S ₁ (m ² ) and the area of the discharge port 52p is S ₂ (m ² ), the area S ₂ of the discharge port 52p with respect to the area S ₁ of the discharge hole 9b is changed. Then, the noise level and COP (coefficient of performance) were tested, and the results shown in FIG. 7 were obtained. From FIG. 7, when setting was made so that 1.2 <(S ₁ / S ₂ ) <3.0, a result satisfying both the noise level and the COP was obtained. That is, the noise level is 1 when (S ₁ / S ₂ ) = 3.0, and gradually decreases below this, and becomes 0.94 when (S ₁ / S ₂ ) = 1.2. As a result, the COP gradually decreases, but noise can be reduced.

  The noise level of the conventional hermetic compressor is represented by 1.01.

Based on such knowledge, when the area of the discharge hole 9b is S ₁ m ² and the area of the discharge port 52p is S ₂ m ² , 1.2 <(S ₁ / S ₂ ) <3.0. Is set to be

Further, as shown in FIG. 8, the volume of the muffler chamber 9 a is V ₁ m ³ , and is formed by one end side of the compression mechanism unit 5 of the electric motor unit 3 and one end side of the compression mechanism unit 5 on the electric motor unit 3 side. By setting the space volume in the sealed container 2 to V ₂ m ³ and n being an integer, V ₂ ≠ (2 + n) V ₁ is set, and the volume ratio is removed from an integer multiple of 2 or more. As shown in FIG. 9, amplification of noise due to resonance can be prevented.

Based on such knowledge, the volume of the muffler chamber 9a is set to V ₁ m ^3, and a sealed container formed by one end side of the compression mechanism unit 5 of the electric motor unit 3 and one end side of the compression mechanism unit 5 on the electric motor unit 3 side. When the space volume in ₂ is V ₂ m ³ and n is an integer, V ₂ ≠ (2 + n) V ₁ is set.

  In addition, since the hermetic compressor 1 has a high pressure in the hermetic container 2, the hermetic terminal 7 is improved in addition to using a thick member that can withstand high pressure.

  For example, as shown in FIG. 10, the sealing terminal 7 provided on the upper portion of the sealed container 2 includes a disk portion 7a, a main body portion 7c including a ring-shaped portion 7b extending in the thickness direction from the disk portion 7a, and a disk. A power supply pin 7d provided in an airtight manner on the portion 7a and a terminal glass portion 7g for fixing the power supply pin 7d are provided.

  As shown in FIG. 11, the disk portion 7a of the sealing terminal 7 is fitted into the mounting hole 2d of the sealing terminal 7 provided in the container upper portion 2a, and is hermetically welded.

  Since the sealing terminal 7 has the above structure and is hermetically welded to the mounting hole 2d, it can withstand high pressure.

As shown in FIG. 12, the end face 7e of the ring-shaped portion 7b is welded at the contact surface between the lower electrode P ₂ of the resistance welding machine (see FIG. 11), and a plane perpendicular to the pressurizing direction by the upper electrode P ₁ On the other hand, it has the inclined surface which inclines at the angle of 1-15 degrees on the disk part side as it goes to the inner peripheral side.

  FIG. 13 shows the correlation between the inclination angle of the end face 7 e and the strain of the sealing terminal 7.

  As shown in FIG. 13, when the inclination angle of the end face 7e is in the range of 1 to 15 °, it becomes equal to or less than the strain limit value causing no problem in use.

By tilting 1 to 15 ° to the end face 7e contact with the lower electrode P ₂ equivalents, during the projection welding, it is easy to easily fit a sealed terminal center and lower electrode center (suppress misalignment).

  On the other hand, if the inclination angle of the end face 7e is out of the range of 1 to 15 °, the pressure resistance is reduced due to the thin wall, and the distortion of the sealing terminal 7 increases. Occurs and a stable welded state cannot be obtained.

  Here, the welding of the sealing terminal 7 to the container upper part 2a will be described.

  As shown in FIG. 11, the disk portion 7a is fitted into the mounting hole 2d provided in the container upper part 2a, and the sealing terminal 7 is attached to the container upper part 2a.

Thereafter, the upper electrode P ₁ of the welder presses the upper container 2a, undergoes an end face 7e lower electrode P _2.

When energized between the upper electrode _{P 1} and the lower electrode _{P 2,} vessel top 2a, the disk portion 7a, the ring-shaped portion 7b, a current in the end face 7e flows. When current flows in this manner, heat is generated by electrical resistance between the container upper portion 2a (the wall surface of the mounting hole 2d) and the disk portion 7a, and the sealed terminal 7 is attached to the container upper portion 2a in an airtight and pressure-resistant manner.

  Since the end face 7e is provided with an inclination of 1 to 15 °, the center of the lower electrode and the center of the sealing terminal can be easily aligned at the time of welding, and the welding operation is facilitated.

  FIG. 14 is a diagram for explaining a vector of deformation of the sealed terminal due to a difference in the inclination angle of the end face.

As shown in FIG. 14, during welding, the force acting on the sealing terminal through the end face having an inclination of 1 to 15 ° is F ₁ , and the vertical component force is F _1V . On the other hand, the force acting on the sealing terminal through the end face inclined at 45 ° is F ₂ , and the vertical component force is F _2V .

When a sealed terminal having an end surface inclination of 1 to 15 ° is used, the vertical component force _F1V is small, the terminal glass portion 7g is not greatly deformed, and the terminal glass portion 7g is not damaged.

On the other hand, when a sealed terminal having an end face inclination of 45 ° is used, the component force in the vertical direction is large in F _2V , the terminal glass portion 7g is not greatly deformed, and the terminal glass portion 7g may be damaged. .

  A first modification of the sealed terminal will be described.

  As shown in FIG. 12, the sealed terminal used in the above embodiment has an inclined surface that is inclined at an angle of 1 to 15 ° as the end surface is directed toward the inner peripheral side, whereas the first modification is an end surface. Has an inclined surface that is inclined at an angle of 1 to 15 ° toward the outer peripheral side.

  For example, as shown in FIG. 15, the sealing terminal 71 of the first modification has an inclined surface that is inclined at an angle of 1 to 15 ° as the end surface 71 e moves toward the outer peripheral side.

  Thereby, by tilting the end surface 7e parallel to the lower electrode surface by 1 to 15 °, it becomes easy to align the center of the lower electrode and the center of the sealing terminal (suppress core misalignment) during projection welding. There is no possibility that the glass part 7g is damaged.

  In addition, since another structure is not different from the sealing terminal shown in FIG. 11, the same code | symbol is attached | subjected to the same part and description is abbreviate | omitted.

  A second modification of the sealed terminal will be described.

  As shown in FIG. 11, the sealing terminal used in the above embodiment has an inclined surface that is inclined at an angle of 1 to 15 ° as the end surface is directed toward the inner peripheral side, whereas the second modification is an end surface. However, it inclines at the angle of 1-15 degrees to the said disk part side as it goes to an inner peripheral side and an outer peripheral side.

  For example, as shown in FIG. 16, the sealing terminal 72 of the first modified example has an inclined surface that is inclined at an angle of 1 to 15 ° as the end surface 72 e moves toward the inner peripheral side and the outer peripheral side.

  Thereby, by tilting the end surface 7e parallel to the lower electrode surface by 1 to 15 °, it becomes easy to align the center of the lower electrode and the center of the sealing terminal (suppress core misalignment) during projection welding. There is no possibility that the glass part 7g is damaged.

  As described above, the hermetic compressor according to the present embodiment realizes a hermetic compressor that can rectify the discharge gas to reduce fluid pulsation and reduce noise propagated outside the hermetic container. Is done.

  Moreover, according to the refrigeration cycle apparatus of the present embodiment, a refrigeration cycle apparatus capable of reducing noise is realized.

  Note that the present invention is not limited to the hermetic compressor and the refrigeration cycle apparatus of the above embodiment. For example, the refrigerant may be a refrigerant other than carbon dioxide.

  DESCRIPTION OF SYMBOLS 1 ... Sealed compressor, 2 ... Sealed container, 2a ... Container upper part, 2b ... Container lower part, 2c ... Container main body, 2d ... Mounting hole, 3 ... Electric motor part, 31 ... Stator, 32 ... Rotor, 4 ... Rotation Shaft, 4a ... eccentric part, 5 ... compression mechanism part, 51 ... cylinder, 52 ... main bearing, 52a ... valve mechanism housing recess, 52b ... discharge valve, 52c ... valve stopper, 52p ... discharge port, 53 ... auxiliary bearing, 54 ... Cylinder chamber, 55 ... Roller, 6 ... Accumulator, 7 ... Sealed terminal, 7a ... Disk part, 7b ... Ring-like part, 7c ... Main body part, 7d ... Power supply pin, 7e ... End face, 7g ... Terminal glass part, 8 ... Lead wire, 8a ... socket, 9 ... discharge muffler, 9a ... muffler chamber, 9b ... discharge hole, 101 ... refrigeration cycle device, 102 ... radiator, 103 ... expansion device, 104 ... evaporator, 105a ... high pressure side piping, 105b ... Low pressure side piping.

Claims (5)

An electric motor part in the sealed container , a cylinder driven by the electric motor part via a rotating shaft to form a cylinder chamber, a roller engaged with an eccentric part of the rotating shaft and rotating eccentrically in the cylinder, together accommodate a compression mechanism portion that have a bearing for supporting the rotary shaft is attached to the cylinder, provided with a discharge port for discharging the refrigerant in the compression chamber of the cylinder chamber to the bearing, opening and closing the discharge port One end portion in the longitudinal direction of the discharge valve and the valve stopper for limiting the lift amount of the discharge valve is fixed to the bearing, and the discharge muffler that covers the discharge valve and the valve stopper to form a muffler chamber is provided in the bearing. In the hermetic compressor attached to the
The discharge muffler is provided with a single discharge hole for discharging the refrigerant in the muffler chamber into the space of the sealed container ,
The discharge hole is a circle having a radius (L / 2) centered on the center of the fixed portion of the valve stopper when viewed from the axial direction of the rotary shaft, where L is the length of the valve stopper in the longitudinal direction. A hermetic compressor characterized by being formed within a range. When the area of the discharge hole of the discharge muffler is S ₁ (m ² ) and the area of the discharge port of the bearing is S ₂ (m ² ),
1.2 <(S ₁ / S ₂ ) <3.0
The hermetic compressor according to claim 1, wherein: The volume of the muffler chamber of the discharge muffler is V ₁ (m ³ ), and the space volume in the sealed container formed by one end side of the compression mechanism part of the electric motor part and one end side of the electric motor part side of the compression mechanism part Is V ₂ (m ³ ) and n is an integer,
V ₂ ≠ (2 + n) V ₁
The hermetic compressor according to claim 1 or 2, characterized in that: The sealed container is provided with a sealed terminal that is fixed by resistance welding and supplies power to the electric motor unit,
This sealed terminal has a disk part, a main body part consisting of a ring-shaped part extending in the thickness direction from the disk part, and a power supply pin airtightly provided on the disk part. The end surface of the ring-shaped portion that becomes the contact surface is 1 to 15 degrees toward the disk portion side toward at least one of the inner peripheral side and the outer peripheral side with respect to a plane orthogonal to the pressing direction by the resistance welder. The hermetic compressor according to claim 1, further comprising an inclined surface inclined at an angle. A hermetic compressor according to any one of claims 1 to 4, the radiator and the expansion device and the refrigeration cycle apparatus characterized by comprising an evaporator.

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