JP2008303887A5 - - Google Patents

Description

Compressor muffler structure and compressor

The present invention relates to a muffler structure of a compressor such as a rotary compressor used in an air conditioner and the like, and a compressor .

  A conventional compressor muffler structure includes an end plate member attached to an opening end of a cylinder body and having a discharge port communicating with the inside of the cylinder body, a reed valve for opening and closing the discharge port of the end plate member, and the end plate And a cup-shaped muffler body attached to the plate member (see Japanese Patent Laid-Open No. 6-2687: Patent Document 1).

  However, in the above-described conventional compressor muffler structure, since the one surface of the end plate member on which the reed valve is provided is flat, the refrigerant gas blown out from the discharge port remains as it is in the discharge port. The air is blown out of the muffler main body through an annular gap at the center of the muffler main body which is substantially directly above.

Thus, the refrigerant gas blown out from the discharge port cannot effectively consume energy inside the muffler body, and there is a problem that noise due to the refrigerant gas cannot be reduced effectively.
Japanese Patent Laid-Open No. 6-2687

Therefore, an object of the present invention is to provide a muffler structure of a compressor and a compressor that can effectively reduce noise caused by refrigerant gas blown out from a discharge port.

In order to solve the above problems, the muffler structure of the compressor of the present invention is
A reed valve that opens and closes a discharge port provided in the end plate member, and a cup-shaped muffler body that covers the reed valve and forms a first throttle portion on the peripheral wall;
An inclined surface that guides the gas discharged from the discharge port toward the inner surface of the first throttle portion is provided in a portion of the end plate member between the tip side of the reed valve and the first throttle portion ,
The inclined surface includes a surface orthogonal to the end surface of the end plate member and facing the discharge port side .

  According to the muffler structure of the compressor of the present invention, the gas (for example, the refrigerant gas) blown out from the discharge port of the end plate member is moved to the leading end side (free end side) of the reed valve by the reed valve. Guided smoothly. Then, the gas directly hits the inclined surface of the end plate member, the direction of the flow is smoothly changed, and energy is consumed. Further, the gas whose flow direction has been changed by the inclined surface collides with the inner surface of the first throttle part of the peripheral wall of the muffler body, consumes energy, and further passes through the first throttle part. To drain energy.

  Thus, by changing the flow direction of the gas a plurality of times, causing the gas to collide a plurality of times, and squeezing the gas at the first throttle portion, the energy of the gas is attenuated, Noise due to the gas can be effectively reduced.

  In one embodiment of the muffler structure of the compressor, the peripheral wall of the muffler body has a second throttle portion on the opposite side of the first throttle portion with respect to the discharge port.

  According to the muffler structure of the compressor of this embodiment, the peripheral wall of the muffler body has the second throttle portion, so that the gas blown out from the discharge port of the end plate member is the first throttle. It repeatedly collides with the inner surface of the part and the inner surface of the second throttle part. As described above, the gas is repeatedly reflected on the inner surface of the first restrictor and the inner surface of the second restrictor, so that the energy of the gas can be further attenuated and the noise caused by the gas can be further reduced. Can be reduced.

  In the muffler structure of the compressor according to one embodiment, the muffler body has a discharge port on the opposite side of the discharge port with respect to the first throttle portion.

  According to the muffler structure of the compressor of this embodiment, since the muffler body has the discharge port, the gas is the first throttle part (or the first throttle part and the second throttle part). After passing through the exhaust, the exhaust from the exhaust body of the muffler body exits, so that noise due to the gas can be reliably reduced.

Moreover, in the compressor of one Embodiment, it has the muffler structure of the said compressor.

According to the compressor of this embodiment, since the compressor has the muffler structure, noise due to the refrigerant gas blown out from the discharge port can be effectively reduced.

According to the muffler structure and the compressor of the compressor of the present invention, the end plate member has the inclined surface, and the peripheral wall of the muffler main body has the first throttle portion. The direction can be changed a plurality of times, the gas can be collided a plurality of times, and the gas can be squeezed by the first restrictor, and the energy of the gas can be attenuated to effectively reduce the noise caused by the gas.

  Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.

  FIG. 1 is a sectional view showing an embodiment of a muffler structure of a compressor according to the present invention. This compressor is a so-called high-pressure dome-type rotary compressor, and has a casing 1 with a compression section 2 on the bottom and a motor 3 on the top. The compressor 6 is driven by the rotor 6 of the motor 3 via the drive shaft 12.

  The compression unit 2 sucks refrigerant gas through an intake pipe 11 from an accumulator (not shown). The refrigerant gas is obtained by controlling a condenser, an expansion mechanism, and an evaporator (not shown) that constitute an air conditioner as an example of a refrigeration system together with the compressor.

  The compressor discharges the compressed high-temperature and high-pressure discharge gas from the compression unit 2 to fill the inside of the casing 1, and passes the motor 3 through the gap between the stator 5 and the rotor 6 of the motor 3. After cooling, it is discharged from the discharge pipe 13 to the outside. Lubricating oil 9 is stored in the lower portion of the high pressure region in the casing 1.

  As shown in FIGS. 1 and 2, the compression section 2 is attached to each of a cylinder body 21 forming a cylinder chamber 22 and upper and lower open ends of the cylinder body 21 to cover the cylinder chamber 22. An upper end plate member 50 and a lower end plate member 24 are provided.

  The drive shaft 12 passes through the upper end plate member 50 and the lower end plate member 24 and enters the cylinder chamber 22.

  A roller 27 fitted to a crank pin 26 provided on the drive shaft 12 is disposed in the cylinder chamber 22 so as to be able to revolve, and a compression action is performed by the revolving motion of the roller 27.

  The cylinder chamber 22 is partitioned by a blade 28 provided integrally with the roller 27. That is, as shown in FIG. 2, in the right chamber of the blade 28, the suction pipe 11 opens on the inner surface of the cylinder chamber 22 to form a suction chamber 22a. On the other hand, in the chamber on the left side of the blade 28, a discharge port 51a shown in FIG. 1 is opened on the inner surface of the cylinder chamber 22 to form a discharge chamber 22b.

  Semi-circular bushes 25, 25 are in close contact with both surfaces of the blade 28 for sealing. Lubrication is performed between the blade 28 and the bushes 25, 25 with the lubricating oil 9.

  The crank pin 26 rotates eccentrically with the drive shaft 12, and the roller 27 fitted to the crank pin 26 contacts the outer peripheral surface of the roller 27 with the inner peripheral surface of the cylinder chamber 22. , Revolve.

  As the roller 27 revolves in the cylinder chamber 22, the blade 28 advances and retreats with both side surfaces of the blade 28 being held by the bushes 25, 25. Then, a low-pressure refrigerant is sucked into the suction chamber 22a from the suction pipe 11, compressed in the discharge chamber 22b to a high pressure, and then a high-pressure refrigerant is discharged from the discharge port 51a.

  As shown in FIGS. 1, 3, and 4, the upper end plate member 50 (hereinafter simply referred to as the end plate member 50) has a disk-shaped main body 51 and an upper portion in the center of the main body 51. And a boss portion 52 provided to the head.

  The main body 51 and the boss 52 are inserted through the drive shaft 12. The main body 51 is provided with the discharge port 51 a communicating with the cylinder chamber 22.

  A plate-like reed valve 31 and a plate-like valve pressing member 32 are provided on an end surface 51c opposite to the cylinder main body 21 in the axial direction of the main body 51. In FIG. 3, the reed valve 31 and the valve pressing member 32 are omitted.

  The reed valve 31 has a fixed end fixed to the end surface 51c of the main body 51 and a free end that opens and closes the discharge port 51a.

  The free end (front end) of the reed valve 31 is elastically deformed according to the pressure of the refrigerant (compressed gas) in the cylinder chamber 22 to open and close the discharge port 51a.

  The valve pressing member 32 cooperates with the end plate member 50 to sandwich the fixed end of the reed valve 31. The valve pressing member 32 suppresses the movement of the reed valve 31 so that the free end of the reed valve 31 is not deformed (oscillated) more than necessary.

  The end surface 51c to which the fixed end of the reed valve 31 is fixed rises to form a seat. Further, the periphery of the discharge port 51a rises to substantially the same height as the seat to form a valve seat.

  The end plate member 50 has an inclined surface 51b that is continuous with the discharge port 51a and faces the discharge port 51a at a position opposite to the fixed end of the reed valve 31 with respect to the discharge port 51a.

  The inclined surface 51b has a substantially rectangular shape. The length of the inclined surface 51b in the radial direction substantially matches the length of the end surface 51c in the radial direction. The circumferential length of the inclined surface 51b is shorter than the radial length of the inclined surface 51b.

  As shown in FIGS. 1, 3, and 5, a cup-type muffler main body 40 is attached to the end plate member 50 so as to cover the end face 51 c of the main body 51. The muffler main body 40 includes an end wall (upper wall) 42 that is substantially parallel to the end surface 51 c of the main body 51, and a peripheral wall 41 that is provided downward around the end wall 42. In FIG. 3, the muffler body 40 is drawn with imaginary lines.

  The peripheral wall 41 of the muffler main body 40 is fitted into the outer peripheral surface of the main body 51 of the end plate member 50.

  The peripheral wall 41 of the muffler body 40 is a first throttle portion 41a that is squeezed radially inward at a position opposite to the discharge port 51a of the end plate member 50 with respect to the inclined surface 51b of the end plate member 50. Have

  The peripheral wall 41 of the muffler main body 40 has a second throttle portion 41b that is narrowed inward at a position opposite to the inclined surface 51b of the end plate member 50 with respect to the discharge port 51a of the end plate member 50. .

  The first diaphragm portion 41a and the second diaphragm portion 41b are opposed to each other and are substantially symmetrical with respect to the axis of the drive shaft 12. That is, the end wall 42 of the muffler body 40 is formed in a gourd shape when viewed from the axial direction.

  The aperture amount of the first aperture portion 41a is larger than the aperture amount of the second aperture portion 41b. That is, the shortest distance between the inner surface of the first throttle portion 41a and the axis of the drive shaft 12 is greater than the shortest distance between the inner surface of the second throttle portion 41b and the axis of the drive shaft 12. small.

  A hole 42a is provided in the center of the end wall 42 of the muffler main body 40, and the boss 52 of the end plate member 50 is inserted into the hole 42a. A gap is provided between the inner peripheral surface of the hole 42 a and the outer peripheral surface of the boss portion 52. This gap forms a discharge port S.

  The discharge port S is at a position opposite to the discharge port 51a of the end plate member 50 with respect to the first throttle portion 41a. That is, the discharge port S is at a position that is substantially symmetrical with the discharge port 51a, with the axis of the drive shaft 12 as the center.

  In other words, the space inside the muffler main body 40 is divided into a discharge region and a non-discharge region by the first throttle portion 41a and the second throttle portion 41b. The discharge region is a region where the discharge port 51a is present. The non-ejection area is an area where the discharge port S is present.

  The muffler main body 40 is fixed to the end surface 51c of the main body 51 of the end plate member 50 by a fixing member 35 (such as a bolt). That is, the fixing member 35 is disposed in the depression of the muffler body 40 formed by the first diaphragm 41a and the depression of the muffler body 40 formed by the second diaphragm 41b. Yes.

  Next, the operation of the muffler structure of the compressor having the above configuration will be described.

  As shown in FIG. 1, the compressed refrigerant gas in the cylinder chamber 22 is blown out from the discharge port 51 a of the end plate member 50 into the muffler body 40.

  At this time, the refrigerant gas is smoothly guided to the leading end side (free end side) of the reed valve 31 by the reed valve 31, and the inclined surface 51b of the end plate member 50 is shown in FIG. In the direction (arrow A direction).

  The refrigerant gas directly strikes the inclined surface 51b of the end plate member 50, smoothly changes the flow direction, and consumes energy. Further, the refrigerant gas whose flow direction has been changed by the inclined surface 51b collides with the inner surface of the first throttle portion 41a of the peripheral wall 41 of the muffler main body 40 to consume energy, and further, the first gas The energy is consumed through the aperture 41a.

  Thus, by changing the flow direction of the refrigerant gas a plurality of times, causing the refrigerant gas to collide a plurality of times, and constricting the refrigerant gas at the first constriction part 41a, the energy of the refrigerant gas. Can be attenuated to effectively reduce noise caused by the refrigerant gas.

  On the other hand, the refrigerant gas that has flowed toward the fixed end of the reed valve 31 collides with the inner surface of the second throttle portion 41 b of the peripheral wall 41 of the muffler body 40. That is, the refrigerant gas repeatedly collides with the inner surface of the first throttle portion 41a and the inner surface of the second throttle portion 41b. Thus, since the refrigerant gas is repeatedly reflected on the inner surface of the first throttle part 41a and the inner surface of the second throttle part 41b, the energy of the refrigerant gas can be further attenuated. Noise due to gas can be further reduced.

  The refrigerant gas passes through the first throttle part 41a and the second throttle part 41b and then flows out of the muffler body 40 from the outlet S of the muffler body 40. Thus, noise due to the refrigerant gas can be reliably reduced.

  Moreover, since the amount of restriction of the first restrictor 41a is larger than the amount of restriction of the second restrictor 41b, the refrigerant gas can be reliably applied to the inner surface of the first restrictor 41a. In addition, an increase in pressure loss due to a reduction in the gas passage area is prevented.

  In addition, this invention is not limited to the above-mentioned embodiment. For example, you may use the muffler structure of this invention for positive displacement compressors other than a swing compressor. Alternatively, the second diaphragm 41b may be omitted and only the first diaphragm 41a may be provided.

It is sectional drawing which shows one Embodiment of the muffler structure of the compressor of this invention. It is a top view of the principal part of a compressor. It is a top view of an end plate member. It is PP sectional drawing of FIG. It is a top view of a muffler main body.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Casing 2 Compression part 3 Motor 9 Lubricating oil 12 Drive shaft 21 Cylinder main body 22 Cylinder chamber 22a Suction chamber 22b Discharge chamber 25 Bush 26 Crankpin 27 Roller 28 Blade 31 Lead valve 32 Valve pressing member 35 Fixing member 40 Muffler main body 41 Circumferential wall 41a First throttle portion 41b Second throttle portion 42 End wall 42a Hole portion 50 End plate member 51 Main body portion 51a Discharge port 51b Inclined surface 51c End surface 52 Boss portion S Discharge port

Claims (4)

A reed valve (31) that opens and closes the discharge port (51a) provided in the end plate member (50), and a cup that covers the reed valve (31) and that forms the first throttle part (41a) on the peripheral wall (41) In the muffler structure of the compressor comprising the muffler body (40) of the type,
Gas discharged from the discharge port (51a) to the portion of the end plate member (50) between the tip side of the reed valve (31) and the first throttle portion (41a) is supplied to the first throttle portion. An inclined surface (51b) for guiding toward the inner surface of (41a) is provided ,
The inclined surface (51b) includes a surface orthogonal to the end surface (51c) of the end plate member (50) and facing the discharge port (51a) . The muffler structure of the compressor according to claim 1,
The compression wall characterized in that the peripheral wall (41) of the muffler body (40) has a second throttle part (41b) on the side opposite to the first throttle part (41a) with respect to the discharge port (51a). The muffler structure of the machine. In the muffler structure of the compressor according to claim 1 or 2,
The muffler structure of the compressor, wherein the muffler body (40) has a discharge port (S) on the opposite side of the discharge port (51a) with respect to the first throttle portion (41a). A compressor having the muffler structure of the compressor according to any one of claims 1 to 3.