JP2016160758A - Hermetic compressor and refrigeration apparatus provided with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hermetic type compressor improving silence effect and a refrigerator installed with the hermetic type compressor.SOLUTION: A hermetic type compressor 10 comprises an electric component 30, a compressing component 20 driven by the electric component 30, a hermetic type container 11 for storing the electric component 30 and the compressing component 20. The compressing component 20 comprises blocks 22a, 22b of which inner spaces have formed compression spaces, a piston 23 driven by the electric component 30 and reciprocated in the compressing spaces, and an intake muffler 40 of which inner space forms a sound muffling space communicated with the compression spaces and there are further provided with members 45, 46 that cause the sound muffling space to be used as a resonance space for reducing sound wave of resonance frequency coinciding with a natural frequency of the hermetic type container 11 through interference and an expansion space for reducing a sound wave of lower frequency than the resonance frequency by expanding a sectional area of the resonance space more than an area of a communication port with the compression space.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a hermetic compressor provided with a suction muffler and a refrigeration apparatus including the same.

  2. Description of the Related Art Conventionally, for example, a hermetic compressor that silences a vibration sound of a suction valve of a cylinder head and a pulsation sound of refrigerant gas by a silencer shown in Patent Document 1 is known. The silencer includes a passage portion that communicates the suction port of the hermetic container and the suction portion of the compressor element, and a plurality of resonators provided along the passage portion. When a sound in a frequency band that is not sufficiently silenced by the silencer is radiated from the suction port to the resonance space that surrounds the compressor body, and this sound resonates in the resonance space, noise having a specific frequency (400 Hz, 600 Hz) in the resonance space is generated. For this reason, the resonator is configured to reduce the sound of a specific frequency in the resonance space.

JP-A-10-184542

  The prior art described in Patent Document 1 still has room for improvement from the viewpoint of further improving the silencing effect. The present invention has been made to solve such problems, and an object of the present invention is to provide a hermetic compressor and a refrigeration apparatus including the hermetic compressor with an improved noise reduction effect.

  A hermetic compressor according to an aspect of the present invention includes an electric element, a compression element driven by the electric element, and a sealed container that accommodates the electric element and the compression element. A block in which a compression space is formed; a piston driven by the electric element to reciprocate in the compression space; and a suction muffler in which a sound deadening space communicating with the compression space is formed. The silence space is lower than the resonance frequency by enlarging the cross-sectional area of the resonance space that reduces the sound wave of the resonance frequency that matches the natural frequency of the sealed container by interference and the area of the communication port with the compression space. A member that also serves as an expansion space that reduces sound waves of a frequency is further provided.

  The present invention has an effect that it is possible to provide a hermetic compressor having the above-described configuration and improving the silencing effect and a refrigeration apparatus including the same.

It is sectional drawing which shows the hermetic compressor which concerns on Embodiment 1 of this invention. It is a top view which shows the rear side member of the suction muffler of FIG. FIG. 3 is a perspective view showing an inhalation muffler cut along line AA in FIG. 2. It is a graph which shows the relationship between the frequency of a sound wave, and the attenuation amount of the sound wave of an inhalation muffler. It is a graph which shows the relationship between the frequency of a sound wave, and the sound pressure level of a hermetic compressor. It is a graph which shows the relationship between the dimension ratio of each plate-shaped member, and the attenuation amount of a sound wave. It is a top view which shows the rear side member of the suction muffler which concerns on Embodiment 5 of this invention. It is a top view which shows the rear side member of the suction muffler which concerns on Embodiment 5 of this invention. It is sectional drawing which shows schematically the refrigerator which concerns on Embodiment 6 of this invention. It is sectional drawing which shows schematically the refrigerator which concerns on Embodiment 6 of this invention.

(Knowledge that became the basis of the present invention)
The present inventors examined improvement of the silencing effect in the hermetic compressor. That is, in a hermetic compressor, in addition to the sound waves of frequencies such as the suction sound of the suction valve and the pulsation sound of the refrigerant gas, the high frequency of 3000 to 4000 Hz such as the vibration sound of the discharge valve and the sliding sound of the piston and shaft. Sound waves are also generated. When this high frequency sound wave matches the natural frequency of the sealed container, the silencer becomes a transmission component and excites vibration of the sealed container. Therefore, not only the noise of the spatial resonance sound in the container but also the noise due to the vibration of the container itself is generated. Moreover, the vibration sound of the container of 3000 to 4000 Hz is generally a sound with good human hearing sensitivity, and this contribution rate to noise is high. For this reason, the fact that this high-pitched noise cannot be reduced is insufficient as a silencing function.

  However, in the silencer of patent document 1, the noise of a specific frequency is reduced by matching the silence frequency of the resonator with the specific frequency of the resonance space. For this reason, noise due to vibration of the sealed container is not considered. In addition, since the specific frequencies are 400 Hz and 600 Hz, it is not possible to reduce noise at higher frequencies. In addition, since the silencer frequency range of this resonator is narrow, even noise of a specific frequency may not be sufficiently silenced due to variations in the silencer frequency range of the resonator caused by manufacturing variations.

  Furthermore, the amount and frequency of sound that is reduced by the silencer depends on the volume of the expansion space. If the silencer which reduces the noise of a specific frequency is provided in a silencer like the silencer of patent document 1, the volume of the expansion space of a silencer will be reduced. Therefore, there is a possibility that the silencer cannot exhibit a sufficient silencing effect.

  Therefore, the present inventors have found that noise due to low-frequency and high-frequency sound waves can be reduced by providing a member that uses the silencer space as an expansion space and a resonance space. The present invention has been made based on this finding.

  A hermetic compressor according to a first aspect of the present invention includes an electric element, a compression element driven by the electric element, and a sealed container that accommodates the electric element and the compression element. A block in which a compression space is formed; a piston that is driven by the electric element to reciprocate in the compression space; and a suction muffler in which a sound deadening space communicating with the compression space is formed. From the resonance frequency, by expanding the cross-sectional area from the area of the communication port with the compression space, the resonance space that reduces the sound wave of the resonance frequency that coincides with the natural frequency of the sealed container by interference, and the cross-sectional area thereof A member that also serves as an expansion space that reduces low-frequency sound waves is further provided.

  In a closed compressor according to a second aspect, in the first aspect, a plate-like member is provided in the silencing space, and the plate-like member has a space on one main surface side of the plate-like member. While partitioning into the space of the other main surface side, you may have the opening part which connects the space of said one main surface side, and the space of the said other main surface side partially.

  A hermetic compressor according to a third aspect includes: an electric element; a compression element driven by the electric element; and a sealed container that accommodates the electric element and the compression element. A block in which a compression space is formed, a piston that is driven by the electric element to reciprocate in the compression space, and a suction muffler in which a noise reduction space that communicates with the compression space is formed. A plate-like member is provided in the space, and the plate-like member partitions the silencing space into a space on one main surface side of the plate-like member and a space on the other main surface side, and the one main surface side And an opening that partially communicates the space on the other main surface side.

  In the hermetic compressor according to the fourth aspect, in the second or third aspect, the dimension of the plate member may be 90% or less with respect to the dimension of the plate member and the opening. Good.

  In the hermetic compressor according to the fifth aspect, in any one of the second to fourth aspects, the size of the opening may change in the longitudinal direction of the plate-like member.

  In a sealed compressor according to a sixth aspect, in any one of the second to fifth aspects, the suction muffler further includes a communication pipe that communicates the silencing space and the compression space, and the plate-like member is A suction port of the communication pipe is disposed in the middle or in the vicinity between the first plate-shaped member and the inner surface of the suction muffler facing the first plate-shaped member. May be.

  In the sealed compressor according to a seventh aspect, in any one of the second to fifth aspects, the suction muffler further includes a tail pipe that communicates the sound deadening space and the sealed container, and the plate-like member is A discharge port of the tail pipe is disposed in the middle or in the vicinity between the second plate-like member and the inner surface of the suction muffler facing the second plate-like member. May be.

  In the sealed compressor according to an eighth aspect, in any one of the second to fifth aspects, the suction muffler includes a communication pipe that communicates the silencing space and the compression space, and the silencing space and the sealed container. And the plate-like member includes a first plate-like member and a second plate-like member, and the suction muffler facing the first plate-like member and the first plate-like member The suction port of the communication pipe is disposed in the middle of or near the inner surface of the suction pipe, and the middle or the space between the second plate-shaped member and the inner surface of the suction muffler facing the second plate-shaped member. The discharge port of the tail pipe may be disposed in the vicinity.

  In a closed compressor according to a ninth aspect, in the eighth aspect, the suction muffler has a first surface portion that faces the sealed container, and a second surface portion that faces the first surface portion. Both the plate-like member and the second plate-like member may be provided so as to protrude from the inner surface of the first surface portion or the second surface portion.

  In a sealed compressor according to a tenth aspect, in the eighth aspect, the suction muffler has a first surface portion that faces the sealed container and a second surface portion that faces the first surface portion, The plate member may be provided so as to protrude from the inner surface of one of the first surface portion and the second surface portion, and the second plate member may be provided so as to protrude from the inner surface of the other surface portion.

  The hermetic compressor according to an eleventh aspect according to the eighth aspect, wherein the suction muffler has a third surface portion on which the tail pipe is formed, and a fourth surface portion facing the third surface portion, Both the first plate-like member and the second plate-like member may be provided so as to protrude from the inner surface of the third surface portion or the fourth surface portion.

  The hermetic compressor according to a twelfth aspect according to the eighth aspect, wherein the suction muffler has a third surface portion on which the tail pipe is formed, and a fourth surface portion facing the third surface portion, The first plate member may be provided to protrude from the inner surface of one of the third surface portion and the fourth surface portion, and the second plate member may be provided to protrude from the inner surface of the other surface portion. .

  In the sealed compressor according to a thirteenth aspect, in any one of the eighth to twelfth aspects, the first plate member and the second plate member may be provided in directions orthogonal to each other.

  In the hermetic compressor according to the fourteenth aspect, in any one of the eighth to twelfth aspects, the first plate member and the second plate member may be provided in directions parallel to each other.

  In a sealed compressor according to a fifteenth aspect, in any one of the second to fourteenth aspects, the compression element further includes a tail pipe that communicates the silencing space and the sealed container. The longitudinal direction may extend from the outlet of the tail tube to the front of the outlet.

  In a sealed compressor according to a sixteenth aspect, in any one of the second to fifteenth aspects, the suction muffler has a lower surface portion, and includes a lower end of the plate-like member extending in the vertical direction and the lower surface portion. A gap may be provided between them.

  In the sealed compressor according to a seventeenth aspect, in any one of the second to sixteenth aspects, the piston may be disposed above the electric element.

  In the hermetic compressor according to an eighteenth aspect, in any one of the second to seventeenth aspects, the electric element may be driven at a plurality of rotation speeds by an inverter drive circuit.

  A refrigeration apparatus according to a nineteenth aspect includes the hermetic compressor according to any one of the first to eighteenth aspects.

  Hereinafter, embodiments of the present invention will be specifically described with reference to the drawings. In the following description, the same or corresponding elements are denoted by the same reference symbols throughout the drawings, and redundant description thereof is omitted.

(Embodiment 1)
First, the configuration of the hermetic compressor 10 according to the first embodiment will be described with reference to FIG. FIG. 1 is a cross-sectional view showing a hermetic compressor 10. In the hermetic compressor 10, the main shaft 21a side of the crankshaft is referred to as a rear side, and the sealed container 11 side is referred to as a front side.

  The hermetic compressor 10 includes a hermetic container 11, a compression element 20 and an electric element 30 accommodated in the hermetic container 11. The compression element 20 and the electric element 30 are elastically supported by the sealed container 11 by the suspension spring 12. In the present embodiment, the piston 23 of the compression element 20 is disposed above the electric element 30.

  The sealed container 11 includes an upper container 11a and a lower container 11b, and is formed, for example, by drawing a steel plate. The upper container 11a has a substantially cylindrical upper side surface portion and a substantially hemispherical upper surface portion. The curvature of the upper surface portion is smaller than that of the upper side surface portion. The lower container 11b has a substantially cylindrical lower side surface portion and a substantially hemispherical lower surface portion. The curvature of the lower surface portion is smaller than the lower side surface portion. The upper container 11a and the lower container 11b are combined and integrated, and the sealed container 11 is provided with an internal space (container space).

  The sealed container 11 is filled with oil and refrigerant gas. The oil is collected at the bottom of the lower container 11 b of the sealed container 11. As the refrigerant gas, for example, hydrocarbon-based R600a having a low global warming potential is used. The sealed container 11 is connected with a suction pipe 13 for sucking refrigerant gas and a discharge pipe 14 for discharging refrigerant gas. The suction pipe 13 connects the sealed container 11 and a low-pressure side pipe (not shown) of the refrigeration apparatus. One end of the suction pipe 13 passes through the wall of the sealed container 11 and is disposed in the container space of the sealed container 11.

  The electric element 30 includes a stator 31 and a rotor 32 disposed so as to be coaxial with the axis of the stator 31. The electric element 30 is supplied with electric power from an inverter drive circuit (not shown) and is driven at a plurality of operating frequencies using an inverter as is well known.

  The compression element 20 includes crankshafts 21a and 21b, blocks 22a and 22b, a piston 23, a connecting portion 24, and the like. The crankshaft includes a main shaft 21a and an eccentric shaft 21b provided on the main shaft 21a. The main shaft 21a is fixed to the rotor 32 of the electric element 30, and the lower end thereof is immersed in oil.

  One end of the connecting portion 24 is rotatably attached to the eccentric shaft 21 b and the other end is connected to the piston 23. The connecting portion 24 converts the rotational motion of the eccentric shaft 21 b into the reciprocating motion of the piston 23. The piston 23 is disposed in the internal space (compression space) of the cylinder 22a and is connected to the eccentric shaft 21b via the connecting portion 24.

  A cylinder 22a and a bearing 22b are integrally formed in the block. The bearing portion 22b rotatably supports the main shaft 21a, and the stator 31 of the electric element 30 is fixed. The cylinder 22a has an internal space (compression space). A valve plate 25, a suction valve 26, and a cylinder head 27 are fixed to the end face of the cylinder 22a by a head bolt 28. The valve plate 25 is provided with a suction hole 25a and a discharge hole (not shown). The discharge hole is opened and closed by a discharge valve (not shown) and connected to the discharge pipe 14. The suction hole 25 a is opened and closed by a suction valve 26 and connected to the communication pipe 43.

  The suction muffler 40 is fixed to the end of the cylinder 22a, and is molded of, for example, a synthetic resin such as PBT mainly added with glass fibers. The suction muffler 40 includes a rear member 41 and a front member 42. The rear member 41 and the front member 42 are combined and integrated to form an internal space (silenced space) in the suction muffler 40. A front main surface portion 42 a (first surface portion) of the front member 42 faces the sealed container 11. The rear side main surface portion 41a (second surface portion) of the rear side member 41 has a front side facing the front side main surface portion 42a through the noise reduction space, and a rear side facing the stator 31 of the electric element 30.

  A communication pipe 43 and a tail pipe 44 are connected to the suction muffler 40. The communication pipe 43 communicates the silencing space and the compression space of the cylinder 22 a, and the tail pipe 44 communicates the silencing space and the container space of the sealed container 11.

  Next, the configuration of the suction muffler 40 will be described with reference to FIGS. 2 and 3. FIG. 2 is a view showing the rear member 41. FIG. 3 is a perspective view showing the suction muffler 40 cut along the line AA in FIG. The left-right direction is defined by looking at the rear member 41 side from the front member 42 side of the suction muffler 40.

  The rear member 41 has a rear main surface portion 41a and four rear side surface portions 41b to 41e rising from the rear main surface portion 41a. The rear main surface portion 41a is substantially rectangular in plan view, and has a shape obtained by bending the plane along the circumferential side surface of the cylindrical stator 31 (FIG. 1). Convex portions 41f are respectively provided at the front ends of the four rear main surface portions 41a, and the convex portions 41f surround the rear main surface portions 41a. The lower rear side surface portion 41c faces the upper rear side surface portion 41b and is bent in a V shape on the lower side. A discharge hole 41g for discharging the oil staying in the suction muffler 40 is provided in the vicinity of the bent position of the lower rear side surface portion 41c. The discharge hole 41g penetrates the rear main surface portion 41a. Yes. The right rear side surface portion 41d and the left rear side surface portion 41e are parallel to each other and are orthogonal to the upper rear side surface portion 41b. In the rear member 41, a portion above the connection position of the communication pipe 43, the tail pipe 44, the first plate member 45, the second plate member 46, and the partition wall 47 are integrally molded.

  The communication tube 43 has a cylindrical shape and is connected to the upper rear side surface portion 41b. This connection position is disposed at the center of the upper rear side surface portion 41b in the left-right direction or in the vicinity thereof, and is disposed on the front side of the upper rear side surface portion 41b in the front-rear direction. The communication pipe 43 extends upward from a connection position with the upper rear side surface portion 41b, and a first discharge port 43a is provided at an end thereof. The first discharge port 43a opens to the rear side, and is connected to the compression space (FIG. 1) of the cylinder 22a via the suction hole 25a (FIG. 1). The communication pipe 43 extends downward to the left from the connection position with the upper rear side surface portion 41b, and further extends from the connection position to the rear side along the rear main surface portion 41a having a bent shape. A first suction port 43b is provided at the end of the communication pipe 43, and the first suction port 43b opens toward the rear side (that is, the rear main surface portion 41a) at the lower left side, and is provided in the sound deadening space. The area of the first suction port 43b is smaller than the area of the silencing space when the suction muffler 40 is cut in the direction orthogonal to the left-right direction (cross-sectional area of the silencing space).

  The tail tube 44 has a cylindrical shape with a rectangular cross section, and is connected to the right rear side surface portion 41d. This connection position is arranged at the center of the rear side surface portion 41d on the right side in the vertical direction or in the vicinity thereof. The tail tube 44 extends horizontally from the connection position to the left side. The second suction port 44a of the tail tube 44 is provided in the right rear side surface portion 41d and opens into the container space (FIG. 1) of the sealed container 11. The second discharge port 44b of the tail pipe 44 is provided in the sound deadening space and faces the rear side surface portion 41e on the left side. The second discharge port 44b is located in the middle of or in the vicinity of the upper rear side surface portion 41b and the lower rear side surface portion 41c in the vertical direction, and is connected to the first suction port 43b of the communication pipe 43 in the horizontal direction. It is located in the middle of the discharge port 43a or in the vicinity thereof. The area of the first discharge port 43a is smaller than the area of the silencing space (cross-sectional area of the silencing space) when the suction muffler 40 is cut in a direction orthogonal to the left-right direction.

  The first plate member 45 is a flat plate that has a constant dimension between the upper surface (one main surface) and the lower surface (the other main surface) and extends linearly in the left-right direction. The first plate-like member 45 is provided so as to protrude from the inner surface of the rear main surface portion 41a, and has an upper surface side silencing space (one main surface side space) and a lower surface side silencing space (the other main surface side space). And is divided. The first plate-like member 45 is provided in the silencing space in parallel to the upper rear side surface portion 41b and substantially in parallel to the lower rear side surface portion 41c. The first plate-like member 45 is disposed so as to sandwich the first suction port 43b of the communication pipe 43 between the upper rear side surface portion 41b. The first suction port 43b is located in the middle or in the vicinity between the first plate-like member 45 and the upper rear side surface portion 41b. The left end of the first plate-like member 45 is connected to the left rear side surface portion 41e, and the right end is located below the second discharge port 44b of the tail tube 44. Therefore, the first plate-like member 45 extends in the longitudinal direction from the second discharge port 44b to the front of the second discharge port 44b.

  As shown in FIG. 3, the rear end of the first plate-like member 45 is fixed to the rear main surface portion 41a, and is bent in the front-rear direction along the bent rear main surface portion 41a. The dimension between the rear end and the front end of the first plate member 45 is constant in the left-right direction, and the front end and the rear end are provided in parallel to each other. The front end of the first plate member 45 is not connected to the front member 42, and a gap (first opening) 45 a is provided between the front end and the front member 42. By changing the dimension between the front end and the front member 42 in the left-right direction, the dimension in the front-rear direction of the first opening 45a is not constant in the left-right direction (the direction in which the first plate-like member 45 extends). The silencing space (space on one main surface side) between the first plate-like member 45 and the upper rear side surface portion 41b, the first plate-like member 45 and the lower side via the first opening 45a. The sound deadening space between the rear side surface portion 41c (the space on the other main surface side) is partially communicated.

  As shown in FIG. 2, the second plate-shaped member 46 is a flat plate that has a constant dimension between the right surface (one main surface) and the left surface (the other main surface) and extends linearly in the vertical direction. . The second plate-like member 46 is provided so as to protrude from the inner surface of the rear main surface portion 41a in the muffling space, and has a right muffling space (one main surface side space) and a left muffing space (the other main surface side). Partition). The second plate-like member 46 is provided in parallel to the right rear side surface portion 41d and the left rear side surface portion 41e. The second plate-like member 46 is disposed so as to sandwich the second discharge port 44b of the tail tube 44 between the left-side rear side surface portion 41e. The second discharge port 44b is located in the middle or in the vicinity between the second plate-like member 46 and the left rear side surface portion 41e. The upper end of the second plate-like member 46 is connected to the tail tube 44, and the lower end is located in the vicinity of the lower rear side surface portion 41c with a slight gap. This gap is used as a discharge path 48 for discharging the oil staying in the suction muffler 40.

  As shown in FIG. 3, the second plate member 46 has a constant dimension between the rear end and the front end in the vertical direction, and the front end is provided in parallel to the rear end. The front end of the second plate-like member 46 is not connected to the front side member 42, and a gap (second opening) 46 a is provided between the front end and the front side member 42. The dimension between the front end and the front member 42 is constant in the vertical direction, and the dimension in the front-rear direction of the second opening 46a is constant in the vertical direction (the direction in which the second plate-shaped member 46 extends) without change. is there. A silencer space (space on one main surface side) between the second plate-like member 46 and the right rear side surface portion 41d, and the second plate-like member 46 and the rear left side through the second opening 46a. The sound deadening space between the side surface portion 41e (the space on the other main surface side) is partially communicated.

  As shown in FIG. 2, the partition wall 47 is a flat plate that has a constant dimension between the right surface and the left surface and extends linearly in the vertical direction. The partition wall 47 rises forward from the rear main surface portion 41a in the silencing space, and is provided in parallel to the right rear side surface portion 41d and the left rear side surface portion 41e. The upper end of the partition wall 47 is connected to the upper rear side surface portion 41 b, and the lower end is connected to the tail tube 44. The partition wall 47 is disposed above the second plate member 46 so as to be linear with the second plate member 46 with the tail tube 44 interposed therebetween. The dimension between the front end and the rear end of the partition wall 47 is substantially equal to the height of the upper rear side surface portion 41b rising from the rear main surface portion 41a. Therefore, in the suction muffler 40 in which the rear side member 41 is covered with the front side member 42, the front end of the partition wall 47 reaches the front main surface portion 42 a, and the partition wall 47 partitions the sound deadening space of the suction muffler 40.

  The front member 42 includes a front main surface portion 42a and four front side surface portions 42b to 42e rising from the front main surface portion 42a. The front main surface portion 42a is substantially rectangular in plan view, and has a shape along the circumferential side surface of the cylindrical sealed container 11 (FIG. 1). The center in the left-right direction of the front main surface portion 42a is recessed to the rear side, and the right and left regions protruding from the recess to the front side are formed with curved surfaces that are curved in the left-right direction. Moreover, the recessed part 42f is each provided in the rear end of the four front side surface parts 42b-42e, and the recessed part 42f surrounds the front side main surface part 42a.

  When the convex portion 41 f of the rear side member 41 is fitted into the concave portion 42 f of the front side member 42, the front side member 42 covers the opening surrounded by the four rear side surface portions 41 b to 41 e of the rear side member 41. As a result, the rear member 41 and the front member 42 are integrally combined to form the suction muffler 40, and a silencer space is provided in the suction muffler 40. In the suction muffler 40, the rear main surface portion 41a of the rear member 41 forms a rear main surface portion 41a of the suction muffler 40, and the front main surface portion 42a of the front member 42 forms a front main surface portion 42a of the suction muffler 40. . The upper rear side surface portion 41b and the upper front side surface portion 42b are flush with each other to form the upper side surface portions 41b and 42b of the suction muffler 40. The lower rear side surface portion 41c and the lower front side surface portion 42c are flush with each other to form the lower side surface portions 41c and 42c of the suction muffler 40. The right rear side surface portion 41d and the right front side surface portion 42d are flush with each other to form the right side surface portions 41d and 42d of the suction muffler 40. The left rear side surface portion 41e and the left front side surface portion 42e are joined flush to form the left side surface portions 41e and 42e of the suction muffler 40.

  This silencing space is also used as a resonance space and an expansion space. That is, by providing the members (the first plate-like member 45 and the second plate-like member 46) in the silence space, the sound wave having a resonance frequency (high-frequency sound wave) that matches the natural frequency of the sealed container 11 is interfered. It is used as a resonance space that is reduced by the above. In addition, since the cross-sectional area of the silencing space is larger than the cross-sectional area of the first suction port 43b, the silencing space is also used as an expansion space for reducing sound waves having a lower frequency (low-frequency sound waves) than high-frequency sound waves. It is done. However, high-frequency sound waves may be reduced in the expansion space.

  In addition, it does not specifically limit about the measuring method of the natural frequency of the airtight container 11, A well-known method can be used. For example, the sealed container 11 is hit with an impulse hammer provided with a force sensor. At the time of this impact, the impact force applied to the sealed container 11 from the force sensor of the impulse hammer is measured. At the same time, the response vibration of the sealed container 11 generated by the impact is measured by the acceleration sensor. Then, the natural frequency of the sealed container 11 is calculated based on the striking force and the response vibration.

  Next, the operation of the hermetic compressor 10 configured as described above will be described with reference to FIGS. 1 and 2. The hermetic compressor 10 causes a current to flow through the stator 31 to generate a magnetic field, and rotates the rotor 32. The main shaft 21a fixed to the rotor 32 and the eccentric shaft 21b connected to the main shaft 21a rotate. This rotational motion is converted into a linear motion by the connecting portion 24, and the piston 23 reciprocates in the compression space of the cylinder 22a.

  When the piston 23 moves in this reciprocating motion from the top dead center in the direction in which the volume of the compression space increases, the refrigerant gas in the compression space expands. As a result, the pressure in the compression space is lower than the suction pressure for sucking the refrigerant gas from the container space of the sealed container 11 and the suction pipe 13 to the muffler space of the suction muffler 40. Due to the difference between the pressure in the compression space and the suction pressure, the suction valve 26 is opened and the suction hole 25a is opened. Thereby, the refrigerant gas in the muffler space and the container space and the refrigerant gas from the suction pipe 13 are sucked into the compression space through the suction hole 25a.

  By this suction, the refrigerant gas returns from the refrigeration apparatus (not shown) and is temporarily opened from the suction pipe 13 to the container space. Most of the refrigerant gas goes to the second suction port 44 a facing the opening of the suction pipe 13, and the remaining refrigerant gas diffuses into the container space of the sealed container 11. The refrigerant gas sucked from the second suction port 44a passes through the tail pipe 44 and flows into the noise reduction space from the second discharge port 44b. Then, the refrigerant gas flows through the silencing space, passes through the communication pipe 43 from the first suction port 43b, and is sucked into the compression space from the opened suction hole 25a through the first discharge port 43a.

  On the other hand, when the piston 23 moves in the reciprocating motion from the bottom dead center in the direction in which the volume of the compression space decreases, the refrigerant gas in the compression space is compressed. As a result, the pressure in the compression space rises and becomes higher than the pressure in the sound deadening space of the suction muffler 40. As a result, due to the difference between the pressure in the compression space and the pressure in the muffler space, the suction valve 26 is closed, the discharge valve is opened, and the discharge hole is opened. The refrigerant gas in the compression space is discharged from the discharge hole to the discharge pipe 14.

  Next, the silencing function of the suction muffler 40 will be described with reference to FIGS. In the hermetic compressor 10, vibration noise is generated by opening and closing the suction valve 26. Further, when the refrigerant gas is sucked from the muffler space into the compression space, the refrigerant gas pulsates due to opening and closing of the suction valve 26 to generate a pulsating sound. The vibration sound of the suction valve 26 and the pulsation sound of the refrigerant gas are sound waves having a low frequency of 400 to 600 Hz, for example. Such low-frequency sound waves are radiated to the muffler space of the suction muffler 40 through the communication pipe 43. When the cross-sectional area suddenly expands when entering the silencing space from the communication pipe 43, the intensity of the low frequency sound wave is attenuated, and the low frequency noise caused by the sound wave can be reduced.

  Further, in the hermetic compressor 10, this vibration noise is generated by opening and closing the discharge valve. Furthermore, since the piston 23 reciprocates in the compression space of the cylinder 22a and the main shaft 21a rotates in the bearing portion 22b, sliding noise of the piston 23 and the main shaft 21a is also generated. The vibration sound of these discharge valves and the sliding sound of the piston 23 and the main shaft 21a are high-frequency sound waves of 3000 to 4000 Hz, for example. This high frequency sound wave is also radiated to the muffler space of the suction muffler 40 through the communication pipe 43.

  However, the frequency of the sound wave attenuated in the silencing space as the expansion space is determined by the length of the silencing space (expansion space). Here, since the length of the silencing space (expansion space) is set so as to attenuate the low frequency sound wave, the high frequency sound wave cannot be sufficiently attenuated in the silencing space (expansion space).

  Therefore, when the remaining high-frequency sound waves are radiated from the muffled space (expansion space) through the tail tube 44 to the container space of the sealed container 11, the sealed container 11 causes natural vibrations and high-frequency noise is generated. To do.

  On the other hand, the suction muffler 40 is provided with the first plate-like member 45 and the second plate-like member 46, so that the silencing space is also used as a resonance space for high-frequency sound waves. Noise caused by the sound wave can be reduced.

  Specifically, the high-frequency sound wave is radiated from the first suction port 43b that opens downward on the left side to the silence space as the resonance space. Some of the high-frequency sound waves, for example, a sound wave having a relatively high frequency of about 4000 Hz, travels toward the first plate-like member 45 located below the first suction port 43b. A part of the sound wave hits the first plate-like member 45, and the remaining sound wave passes through the first opening 45 a of the first plate-like member 45. The sound wave that hits the first plate-like member 45 is reflected by the first plate-like member 45 toward the upper side surface portions 41b and 42b, and further reflected by the upper side surface portion 41b and 42b to be reflected on the first plate-like member 45. Head. The sound wave that has passed through the first opening 45a of the first plate-like member 45 is reflected by the lower side surface portions 41c and 42c, travels toward the first plate-like member 45, passes through the first opening 45a, and passes through the upper side. Reflected by the side portions 41 b and 42 b and heading toward the first plate-like member 45.

  As described above, the sound wave reflected by the first plate member 45 and the first opening 45a of the first plate member 45 pass between the upper side surface portions 41b and 42b and the lower side surface portions 41c and 42c. Then, there are sound waves reflected by the lower side surface portions 41c and 42c. When these sound waves overlap with their phases shifted, the sound waves interfere so as to weaken each other. When the first suction port 43b is located in the middle or in the vicinity between the first plate-like member 45 and the upper side surface portions 41b and 42b, these sound waves are overlapped so as to weaken each other by shifting their phases greatly, and high frequency Attenuates sound waves. Since the sound wave of about 4000 Hz is equal to the natural frequency of the upper surface portion of the upper container 11a, for example, resonance noise in the upper surface portion of the upper container 11a due to this sound wave can be reduced.

  In addition, the remaining sound wave among the high frequency sound waves radiated from the first suction port 43b, for example, a sound wave having a relatively low frequency of about 3000 Hz, the left side surface portion 41e located on the left side of the first suction port 43b, Reflects toward 42e. A part of the reflected sound wave hits the second plate member 46, and the remaining sound wave passes through the second opening 46 a of the second plate member 46. The sound wave that hits the second plate-like member 46 is reflected by the second plate-like member 46 toward the left side surface portions 41e and 42e, and further reflected by the left side surface portions 41e and 42e and reflected on the second plate-like member 46. Head. The sound wave that has passed through the second opening 46a of the second plate-shaped member 46 is reflected by the right side surface portions 41d and 42d, travels toward the second plate-shaped member 46, passes through the second opening portion 46a, and then is Reflected by the portions 41e and 42e and directed toward the second plate-like member 46.

  Thus, between the left side surface portions 41e and 42e and the right side surface portions 41d and 42d, the sound wave reflected by the second plate member 46 and the second opening 46a of the second plate member 46 pass. And sound waves reflected by the right side surfaces 41d and 42d. When these sound waves overlap with their phases shifted, the sound waves interfere so as to weaken each other. When the second discharge port 44b is located in the middle or in the vicinity between the second plate-like member 46 and the left side surface portions 41e, 42e, these sound waves are overlapped so as to weaken each other by shifting their phases greatly, and the high frequency Attenuates sound waves. Since the sound wave of about 3000 Hz is equal to the natural frequency of the lower surface portion of the lower container 11b, for example, resonance noise in the lower surface portion of the lower container 11b caused by this sound wave can be reduced.

  As a result, it is possible to reduce high-frequency sound waves from the silenced space (resonance space) through the tail tube 44 and radiate to the container space of the sealed container 11 and to prevent high-frequency noise due to the natural vibration of the sealed container 11. Can do. This will be described with reference to FIG. 4 and FIG.

  FIG. 4 is a graph showing the attenuation of sound waves of the suction muffler 40 alone. The horizontal axis in FIG. 4 indicates the frequency of white noise (sound wave) emitted from the first discharge port 43a. The attenuation amount (dB) on the vertical axis is obtained by subtracting the strength of sound waves when no suction muffler is provided from the strength of sound waves when the suction muffler is provided. The sound wave intensity (dB) was obtained by measuring white noise (sound wave) emitted from the first discharge port 43 a of the communication tube 43 at the second suction port 44 a of the tail tube 44. In the vertical axis of FIG. 4, the value above 0 indicates a positive value, and the value below 0 indicates a negative value. For this reason, when the attenuation amount of the sound wave is a positive value larger than 0, the intensity of the sound wave when the inhalation muffler is not provided is larger than the intensity of the sound wave when the inhalation muffler is provided. Therefore, it is shown that the provision of the suction muffler reduces the intensity of sound waves and improves the acoustic characteristics.

  The broken line indicates the attenuation amount of the sound wave by the suction muffler of the conventional example in which the first plate member 45 and the second plate member 46 are not provided. As shown by the broken line, the attenuation at a frequency of 3000 to 4000 Hz shows a positive value larger than 0, and the sound wave is strengthened by using the suction muffler of the conventional example. This shows that the acoustic characteristics of the suction muffler 40 are deteriorated by providing the conventional suction muffler 40.

  On the other hand, the solid line indicates the attenuation of sound waves by the suction muffler 40 of the embodiment in which the first plate-like member 45 and the second plate-like member 46 are provided. As shown by the solid line, the attenuation amount at a frequency of 3000 to 4000 Hz shows a negative value smaller than 0, and the sound wave is attenuated by using the suction muffler 40 of the embodiment. This shows that the acoustic characteristics of the suction muffler 40 are improved by providing the suction muffler 40 of the embodiment.

  Moreover, the range which exhibits an attenuation function is over 3000-4000 Hz and a wide frequency range. Thus, by providing the first plate-like member 45 and the second plate-like member 46 in the suction muffler 40, sound waves having a frequency of 3000 to 4000 Hz are reduced.

  Furthermore, based on the relationship between the attenuation amount of the sound wave and the frequency of the sound wave, it can be determined that the silence space is also used as the resonance space and the expansion space.

  That is, the suction muffler 40 of the embodiment provided with the plate-like members 45 and 46 having the openings 45a and 46a, the suction muffler of the conventional example not provided with the plate-like member, and the plate-like member having no opening. For the suction muffler of the comparative example provided with the sound wave attenuation amount is acquired.

  Further, since the attenuation amount of the sound wave of the suction muffler of the conventional example is smaller than that of the suction muffler 40 of the embodiment, a resonance space is formed by the plate-like members 45 and 46 in the silencing space of the suction muffler 40 of the embodiment. I understand.

  Further, since the attenuation amount of the sound wave of the suction muffler of the comparative example is smaller than that of the suction muffler 40 of the embodiment, the volume of the expansion space is reduced by the plate-like member having no opening in the silenced space of the comparative example. You can see that

  Thus, it can be seen that the attenuation amount of the suction muffler 40 of the embodiment is larger than the suction muffler of the conventional example and the suction muffler of the comparative example, so that the sound deadening space is also used as the resonance space and the expansion space.

  FIG. 5 is a graph showing the relationship between the sound pressure level of the hermetic compressor 10 and the frequency of sound waves. The broken line shown in FIG. 5 indicates the sound pressure level of noise in the hermetic compressor 10 having the conventional suction muffler in which the first plate member 45 and the second plate member 46 are not provided. A solid line indicates a sound pressure level of noise in the hermetic compressor 10 including the suction muffler 40 of the embodiment provided with the first plate-like member 45 and the second plate-like member 46.

  At a sound wave frequency of 3000 Hz or higher, the solid sound pressure level was lower than the broken sound pressure level. For example, at a frequency of 3000 Hz, the sound pressure level indicated by the solid line is approximately 3.1 dB lower than the sound pressure level indicated by the broken line. At a frequency of 4000 Hz, the sound pressure level indicated by the solid line was approximately 8.2 dB lower than the sound pressure level indicated by the broken line. At a frequency of 6300 Hz, the sound pressure level indicated by the solid line was approximately 3.0 dB lower than the sound pressure level indicated by the broken line. At a frequency of 8000 Hz, the solid sound pressure level was about 3.5 dB lower than the broken sound pressure level.

  Thus, also in the hermetic compressor 10, the resonance of the primary eigenvalue of the hermetic container 11 of 3000 to 4000 Hz can be suppressed by the suction muffler 40. Further, by suppressing the resonance of the primary eigenvalue, the resonance of the secondary and tertiary eigenvalues of 6000 to 8000 Hz can also be suppressed. Moreover, the sound pressure level in a wide high frequency range of 8000 Hz or higher can also be reduced.

  The sound wave attenuation function by the suction muffler 40 depends on the dimensions of the first opening 45 a of the first plate member 45 and the second opening 46 a of the second plate member 46. This will be described with reference to FIG.

  FIG. 6 is a graph showing the relationship between the dimensional ratio of the plate-like members 45 and 46 and the attenuation amount of sound waves. The vertical axis represents the attenuation (dB) of sound waves of 3000 to 4000 Hz, and the horizontal axis represents the dimensional ratio of the plate-like members 45 and 46. The dimensional ratio of each plate-like member 45, 46 is relative to the dimension in the front-rear direction of the muffler space (resonance space) of the suction muffler 40 (the size of each plate-like member 45, 46 and each opening 45a, 46a). The ratio of the dimension of each plate-like member 45, 46 in the front-rear direction. The dimension of the silencing space (resonance space) in the front-rear direction is the dimension between the front main surface part 42a and the rear main surface part 41a of the suction muffler 40, and the dimension in the front-rear direction of each plate member 45, 46 is It is a dimension between the front end and the rear end of the plate-like members 45 and 46. In the graph, points are measured values of the test, and lines are approximate curves drawn based on the measured values.

  In FIG. 6, the dimensional ratio of each plate-like member 45, 46 is 0, that is, when there is no plate-like member 45, 46, the attenuation is almost zero, and the dimensional ratio of each plate-like member 45, 46 is The amount of attenuation increases as the size of each plate-like member 45, 46 increases in the front-rear direction. When the dimensional ratio of each plate-like member 45, 46 is 50% and the dimension in the front-rear direction of each plate-like member 45, 46 is equal to the dimension in the front-rear direction of each opening 45a, 46a, the amount of attenuation is the largest. Become.

  Furthermore, the amount of attenuation decreases as the dimensional ratio of each plate-like member 45, 46 increases and the dimension in the front-rear direction of each plate-like member 45, 46 increases. Thus, the smaller the difference between the dimension in the front-rear direction of each plate-like member 45, 46 and the dimension in the front-rear direction of each opening 45a, 46a, the sound wave reflected by each plate-like member 45, 46 and each opening The amount of cancellation with the sound waves that have passed through 45a and 46a increases, and the attenuation amount of high-frequency sound waves increases.

  For example, when the ratio of the largest attenuation of sound waves is 100%, the ratio of the attenuation of sound waves is about 25% or more when the dimensional ratio of the plate-like members 45 and 46 is 5% or more and 90% or less. A dimensional ratio of 5% to 90% is preferable. Furthermore, when the dimensional ratio between the plate-like members 45 and 46 is 10% or more and 85% or less, the ratio of the attenuation amount of sound waves is about 50% or more. Furthermore, when the dimensional ratio of the plate-like members 45 and 46 is 20% or more and 75% or less, the ratio of the attenuation amount of the sound wave is about 75% or more, and therefore the dimensional ratio of 20% or more and 75% or less is even more preferable.

  As described above, according to the embodiment, the sound wave having the frequency equal to the natural frequency of the sealed container 11 is reduced in the suction muffler 40. For this reason, the situation where the suction muffler 40 resonates at a frequency equal to the natural frequency and the suction muffler 40 becomes a vibration source to excite the vibration of the sealed container 11 can be prevented.

  That is, the first plate-like member 45 and the second plate-like member 46 are provided in the silencing space of the suction muffler 40. Thereby, the silencing space functions as a resonance space. In this resonance space, the sound waves reflected by the plate-like members 45 and 46 and the sound waves reflected by the side surfaces of the suction muffler 40 are overlapped so as to deviate from each other in phase, so that high-frequency sound waves can be attenuated. it can. As a result, high-frequency sound waves radiated from the muffled space (resonance space) to the container space of the sealed container 11 are reduced, and high-frequency noise is prevented from being generated by the natural vibration of the sealed container 11 caused by the sound waves. can do.

  Moreover, since the sound of 3000 to 4000 Hz, which has good sensitivity for human hearing, can be reduced, the noise reduction effect is excellent. Moreover, since each plate-like member 45 and 46 is only provided in the muffling space (resonance space), the number of parts and the number of work steps are not increased, and an increase in cost can be suppressed.

  Furthermore, the position of each plate-like member 45, 46 or the shape of the sealed container 11 varies due to variations in manufacturing, and the damping frequency and the natural vibration of the sealed container 11 due to each plate-like member 45, 46 are not uniform. is there. Even in such a case, since the attenuation function by the respective plate-like members 45 and 46 extends over a wide frequency range, the high-frequency sound wave is attenuated and high due to the natural vibration of the sealed container 11 caused by this sound wave. Generation of noise at a frequency can be prevented.

  In addition, the silencing space is used both as a resonance space and an expansion space. For this reason, it is possible to reduce low-frequency sound waves and high-frequency sound waves without increasing the size of the hermetic compressor 10, and to suppress noise associated therewith.

  Furthermore, since the size of each plate-like member 45, 46 is very small compared to the sound-deadening space as the expansion space, the volume of the sound-deadening space (expansion space) is not substantially reduced by each plate-like member 45, 46. Therefore, the silencing effect with respect to the low frequency sound wave is sufficiently exhibited without increasing the size of the suction muffler 40.

  The first plate 45 is provided with a first opening 45a, and the second plate 46 is provided with a second opening 46a. As a result, the sound waves reflected by the plate-like members 45 and 46 and the sound waves that have passed through the openings 45a and 46a overlap each other more effectively so as to be shifted in phase and attenuate high-frequency sound waves. it can. As a result, the effect of reducing high frequency noise is further improved.

  The first plate-like member 45 is arranged so that the first suction port 43b is located in the middle or in the vicinity between the first plate-like member 45 and the upper rear side surface portion 41b. The 2nd discharge outlet 44b is located in the middle between the 2nd plate-shaped member 46 and the left side surface parts 41e and 42e, or its vicinity. As a result, the sound waves reflected by the plate-like members 45 and 46 and the sound waves reflected by the side surfaces of the suction muffler 40 can be superimposed more efficiently so as to weaken each other, and the effect of reducing high-frequency noise can be reduced. Further improvement is achieved.

  Although the longitudinal dimension of the first plate-like member 45 is constant, the position (height) of the front end of the first plate-like member 45 is changed in the left-right direction by bending the rear main surface portion 41a of the suction muffler 40. It changes, and the dimension of the front-back direction of the 1st opening part 45a is not constant in the left-right direction. For this reason, the area | region (left side area | region of the front side member 42) facing the front end of the 1st plate-shaped member 45 of the front side member 42 can be formed in the curved surface curved in the left-right direction. Therefore, since the rigidity of the curved surface is higher than that of the flat surface, the vibration of the front member 42 can be suppressed, and the noise caused by the vibration of the suction muffler 40 can be reduced.

  In the suction muffler 40, the plate-like members 45 and 46 are provided on the rear member 41, and the first suction port 43b of the communication pipe 43 opens toward the rear main surface portion 41a. For this reason, the high-frequency sound wave radiated from the first suction port 43 b efficiently hits and reflects the plate-like members 45 and 46. Therefore, the noise caused by the high frequency sound wave can be further reduced by the suction muffler 40.

  Further, each of the plate-like members 45 and 46 and the tail tube 44 are provided on the rear main surface portion 41a in a planar shape. Accordingly, the rigidity of the planar member is lower than that of the curved surface, but the rigidity of the rear member 41 is improved by the plate-like members 45 and 46 and the tail tube 44. As a result, vibration of the suction muffler 40 can be suppressed, and noise resulting from this vibration can be suppressed.

  The first plate member 45 extends in the left-right direction, and the second plate member 46 extends in the up-down direction. As described above, the plate-like members 45 and 46 extend in the orthogonal direction, and the extending directions of the plate-like members 45 and 46 are different, so that sound waves in a wide frequency range can be reduced.

  The first plate-like member 45 and the tail tube 44 are provided on the rear main surface portion 41a. Thereby, the refrigerant gas that has flowed into the silencing space from the second discharge port 44 b can be smoothly guided to the first suction port 43 b of the communication pipe 43 along the first plate-like member 45. Therefore, the volumetric efficiency of the refrigerant gas of the hermetic compressor 10 is improved.

  The right end of the first plate-like member 45 is located below the second discharge port 44 b of the tail pipe 44. Thereby, more refrigerant gas flowing in from the second discharge port 44b can be guided along the first plate member 45 to the first suction port 43b. For this reason, the volumetric efficiency of the refrigerant gas of the hermetic compressor 10 is further improved.

  A gap (discharge path) 48 is provided between the lower end of the second plate-like member 46 and the lower rear side surface portion 41c, and the rear main surface portion 41a is located near the bent position of the lower rear side surface portion 41c. There is provided a discharge hole 41g penetrating through. For this reason, the oil staying in the suction muffler 40 is discharged through the discharge hole 48g through the discharge path 48 along the lower rear side surface portion 41c. Therefore, it is possible to suppress a reduction in the silencing function of the suction muffler 40 due to the oil retained in the suction muffler 40.

  Further, the piston 23 of the compression element 20 is disposed above the electric element 30. The vibration generated by the reciprocating motion of the piston 23 is considerably canceled by a balance weight (not shown), but a part of the vibration remains. The vibration remaining in this way causes the blocks 22a and 22b to vibrate as a reaction. The behavior of this vibration is completely different between the upper part of the compression element 20 near the piston 23 and the lower part of the compression element 20 near the suspension spring 12. That is, the upper portion of the compression element 20 directly receives the reaction of the piston 23 and vibrates greatly. On the other hand, since the lower part of the compression element 20 is supported by the suspension spring 12 via the electric element 30, the amplitude thereof is reduced. This reduced vibration is further attenuated by the suspension spring 12 and transmitted to the sealed container 11, so that the vibration of the sealed container 11 can be reduced.

  In the above embodiment, the piston 23 of the compression element 20 is disposed above the electric element 30, but the piston 23 may be disposed below the electric element 30. In this case, when the reciprocating motion of the piston 23 and the suspension spring 12 are close to each other, the vibrations of the blocks 22a and 22b increase, and high-frequency noise is generated. On the other hand, since the acoustic characteristics of 3000 to 4000 Hz are improved by the suction muffler 40 provided with the plate-like members 45 and 46, noise caused by these high-frequency sound waves can be reduced.

  Further, an inverter drive circuit (not shown) may be provided at a power supply terminal (not shown) of the electric element 30. In this case, the rotor 32 of the electric element 30 is driven at a plurality of rotation speeds with respect to the stator 31 by the inverter drive circuit.

  When the inverter 32 is driven by the inverter drive circuit at a rotational speed exceeding the frequency of the commercial power supply, the circulation amount of the refrigerant gas increases, and the opening degree of the intake valve 26 and the discharge valve increases. In addition, the number of sliding operations per unit time of the piston 23 and the crankshafts 21a and 21b increases, and high-frequency noise increases. On the other hand, since the suction muffler 40 has improved acoustic characteristics from 3000 Hz to 4000 Hz, noise due to these high frequency sound waves can be further reduced.

  On the other hand, even when the rotor 32 is driven by the inverter drive circuit at a rotational speed equal to or lower than the frequency of the commercial power supply, the suction muffler 40 improves the acoustic characteristics from 3000 Hz to 4000 Hz. Therefore, it is possible to further reduce the noise caused by these high frequency sound waves.

(Embodiment 2)
In the hermetic compressor 10 according to the first embodiment, the suction muffler 40 is provided with both the first plate-like member 45 and the second plate-like member 46. In contrast, in the hermetic compressor 10 according to the second embodiment, the suction muffler 40 may be provided with only the first plate member 45 without being provided with the second plate member 46, The first muffler 40 may not be provided with the first plate member 45 but only the second plate member 46 may be provided.

  In any case, the frequency range of the sound wave attenuated by the suction muffler 40 is narrower than that of the suction muffler 40 in which both plate-like members 45 and 46 are provided. However, the suction muffler 40 provided with only one of the plate-like members 45 and 46 can sufficiently attenuate the noise of the hermetic compressor 10 since the frequency range of sound waves that can be attenuated is wide.

(Embodiment 3)
In the hermetic compressor 10 according to the first embodiment, the first plate member 45 and the second plate member 46 are provided so as to protrude from the inner surface of the rear main surface portion 41a (second surface portion). In contrast, in the hermetic compressor 10 according to the third embodiment, at least one of the first plate-like member 45 and the second plate-like member 46 is from the inner surface of the front main surface portion 42a (first surface portion). It may be provided protruding.

  That is, both the first plate-like member 45 and the second plate-like member 46 may be provided on the front main surface portion 42a. Moreover, the 1st plate-shaped member 45 may be provided in the rear side main surface part 41a, and the 2nd plate-shaped member 46 may be provided in the front side main surface part 42a. Moreover, the 1st plate-shaped member 45 may be provided in the front side main surface part 42a, and the 2nd plate-shaped member 46 may be provided in the back side main surface part 41a.

  When both or one of the first plate member 45 and the second plate member 46 is provided on the front main surface portion 42a, the rigidity of the front member 42 formed in a curved surface shape is set to each plate member 45, 46. To further improve. Thereby, since the rigidity in the whole suction muffler 40 increases, the surface vibration of the suction muffler 40 can be suppressed and noise due to this vibration can be prevented.

  In the third embodiment, as in the second embodiment, only one of the first plate-like member 45 and the second plate-like member 46 may be provided in the suction muffler 40.

(Embodiment 4)
In the hermetic compressor 10 according to the first embodiment, the plate-like members 45 and 46 are provided so as to protrude from the inner surface of the rear main surface portion 41a (third surface portion) where the tail tube 44 is formed. . That is, the plate-like members 45 and 46 and the tail tube 44 are formed on the same main surface portion. On the other hand, in the hermetic compressor 10 according to the fourth embodiment, each of the plate-like members 45 and 46 has a main surface portion (fourth surface portion) facing the main surface portion (third surface portion) on which the tail tube 44 is formed. It may be provided so as to protrude from the inner surface of the surface portion. That is, the plate-like members 45 and 46 and the tail tube 44 may be formed on different main surface portions.

  That is, the plate-like members 45 and 46 may be provided on the rear main surface portion 41a, the tail pipe 44 may be provided on the front main surface portion 42a, and the plate-like members 45 and 46 may be provided on the front main surface portion 42a. The tube 44 may be provided on the rear main surface portion 41a. In the fourth embodiment, as in the second embodiment, only one of the first plate-like member 45 and the second plate-like member 46 may be provided in the suction muffler 40.

(Embodiment 5)
In the hermetic compressor 10 according to the first embodiment, the first plate member 45 and the second plate member 46 are provided in different orthogonal directions. On the other hand, in the hermetic compressor 10 according to the fifth embodiment, the directions of the first plate member 45 and the second plate member 46 are not limited to this. For example, the first plate member 45 and the second plate member 46 may be provided in parallel and in the same direction.

  In the example shown in FIG. 7, the first suction port 43b of the communication tube 43 and the second discharge port 44b of the tail tube 44 open in the same direction, and their positions in the left-right direction coincide. In this case, the distance between the first suction port 43b and the left side surface portions 41e, 42e facing each other is equal to the distance between the second discharge port 44b and the left side surface portions 41e, 42e facing each other.

  Thus, the wavelength of the standing wave formed between the first suction port 43b of the communication pipe 43 and the left side surface portion 41e facing the first suction port 43b, the second discharge port 44b of the tail pipe 44, and the first The wavelength of the standing wave formed between the left side surface portion 41e facing the two discharge ports 44b is the same. For this reason, the first suction port 43b and the second discharge port 44b are shared so that they are arranged in the middle or in the vicinity between one plate member (shared plate member) 45, 46 and the left side surface portion 41e. Plate members 45 and 46 are provided. Therefore, the sound waves reflected by the shared plate-like members 45 and 46 and the sound waves reflected by the left side surface portions 41e and 42e and the right side surface portions 41d and 42d are overlapped so as to be weakened. For this reason, a high frequency sound wave can be attenuated and the noise of the airtight container 11 resulting from this can be reduced.

  Further, the first plate-like member 45 and the second plate-like member 46 can be shared by one common plate-like member 45, 46, and the number of parts can be reduced.

  In the example shown in FIG. 8, as in the example shown in FIG. 7, the first suction port 43 b of the communication pipe 43 and the second discharge port 44 b of the tail pipe 44 open in the same direction. The position in the direction is different. In this case, since the first suction port 43b is located on the left side of the second discharge port 44b, the distance between the first suction port 43b and the left side surface portions 41e and 42e opposite to the first suction port 43b is the second discharge port 44b. And the distance between the left side surface portions 41e and 42e facing each other.

  Thus, the wavelength of the standing wave formed between the first suction port 43b of the communication pipe 43 and the left side surface portion 41e facing the first suction port 43b, the second discharge port 44b of the tail pipe 44, and the first The wavelength of the standing wave formed between the left side surface portion 41e facing the two discharge ports 44b is different. For this reason, the 1st plate-shaped member 45 is arrange | positioned so that the 1st inlet 43b may become the middle between the 1st plate-shaped member 45 and the left side surface part 41e, or its vicinity. In addition, the second plate-like member 46 is arranged so that the second discharge port 44b is in the middle or the vicinity between the second plate-like member 46 and the left side surface portion 41e. Therefore, the sound waves reflected by the plate-like members 45 and 46 and the sound waves reflected by the left side surface portions 41e and 42e and the right side surface portions 41d and 42d are overlapped so as to weaken each other. For this reason, a high frequency sound wave can be attenuated and the noise of the airtight container 11 resulting from this can be reduced.

  In the fifth embodiment, as in the second embodiment, only one of the first plate-like member 45 and the second plate-like member 46 may be provided on the suction muffler 40. In the fifth embodiment, as in the third embodiment, either the first plate member 45 or the second plate member 46 may be provided on the front member 42. Further, in the fifth embodiment, as in the fourth embodiment, the plate-like members 45 and 46 may be provided on the side of the suction muffler 40 different from the tail tube 44.

(Embodiment 6)
A refrigerator 50 according to the sixth embodiment is a refrigeration apparatus including the hermetic compressor 10 according to any of the first to fifth embodiments. FIG. 9 is a cross-sectional view schematically showing a refrigerator 50 according to the sixth embodiment. As shown in FIG. 9, the refrigerator 50 includes a heat insulating box 51 and a door 52. In addition, the surface of the heat insulation box 51 to which the door 52 is attached is referred to as a front surface, and the opposite surface is referred to as a back surface.

  The heat insulating box 51 has a heat insulating space inside. For example, the heat insulation space is divided by the partition plate 53 into an upper heat insulation space (refrigeration room) and a lower heat insulation space (freezer room). These heat insulation spaces are connected to each other by a duct (not shown), and the air in each heat insulation space is movable by the duct. A temperature sensor (not shown) is provided in at least one of the upper heat insulating space and the lower heat insulating space.

  The heat insulating box 51 is provided with a recessed portion at the corner between the back surface and the lower surface, and the hermetic compressor 10 is disposed in the recessed portion. Further, a condenser (not shown) is disposed on the side surface of the heat insulation box 51 and the capillary 54 which is a decompressor is disposed on the back surface of the heat insulation box 51. An evaporator 55 is disposed on the back surface of the lower heat insulating space. The hermetic compressor 10, the condenser, the capillary 54, and the evaporator 55 are connected in a ring shape by a pipe 57 to constitute a refrigeration cycle.

  The heat insulation box 51 is provided with a control device (not shown), and a temperature sensor is connected to the control device. Further, the hermetic compressor 10, the condenser, the capillary 54, and the evaporator 55 are connected to the control device, and the control device controls them based on the detection value of the temperature sensor.

  A door 52 is attached to each of the upper heat insulating space and the lower heat insulating space so that the opening can be opened and closed. Gaskets are disposed between the doors 52 and the heat insulating box 51, thereby maintaining the airtightness of the heat insulating spaces.

  Next, the operation of the refrigeration cycle in the refrigerator 50 will be described. The control device starts and stops the cooling operation based on the detection signal from the temperature sensor. When the cooling operation is started, the refrigerant gas is compressed to high temperature and high pressure by the reciprocating motion of the piston 23 (FIG. 1) in the hermetic compressor 10, and is sent from the discharge pipe 14 (FIG. 1) to the refrigeration cycle through the pipe 57. It is done. This high-temperature and high-pressure gaseous refrigerant gas is condensed and liquefied when heat is released by the condenser. The liquid refrigerant gas is decompressed by the capillary 54 to become a low temperature and a low pressure, and reaches the evaporator 55. As a result, the refrigerant gas having reached a high temperature evaporates and returns to the hermetic compressor 10 through the pipe 57. On the other hand, the cooled air is distributed to each heat insulation space by a duct, and each heat insulation space is cooled.

  The hermetic compressor 10 of the refrigerator 50 is provided with a first plate member 45 and a second plate member 46. For this reason, the effect | action similar to Embodiment 1 is shown. For example, noise caused by high frequency sound waves can be reduced. Further, since the volume of the expansion space is not substantially reduced by the plate-like members 45 and 46, noise due to low-frequency sound waves can be sufficiently reduced without increasing the size of the suction muffler 40.

  In the sixth embodiment, the hermetic compressor 10 is provided at the lower part of the refrigerator 50. However, the hermetic compressor 10 may be provided at the upper back of the refrigerator 50 as shown in FIG. As shown in FIG. 10, the heat insulation box 51 is provided with a recessed portion at the corner between the back surface and the upper surface, and the hermetic compressor 10 is elastically supported by the recessed portion. In this case, the hermetic compressor 10 provided at the upper back of the refrigerator 50 is positioned close to the ear when a person stands. For this reason, the noise reduction effect by the suction muffler 40 can be exhibited more.

  Further, in the hermetic compressor 10 of the sixth embodiment, as in the second embodiment, only one of the first plate member 45 and the second plate member 46 is provided in the suction muffler 40. Also good. Further, in the hermetic compressor 10 of the sixth embodiment, even if either the first plate-like member 45 or the second plate-like member 46 is provided on the front member 42 as in the third embodiment. Good. Further, in the hermetic compressor 10 according to the sixth embodiment, the plate-like members 45 and 46 may be provided on the suction muffler 40 side different from the tail tube 44 as in the fourth embodiment. In the hermetic compressor 10 of the sixth embodiment, the first plate member 45 and the second plate member 46 may be provided in the same direction as in the fifth embodiment.

  Furthermore, in the said Embodiment 6, although the refrigerator 50 was used as a refrigeration apparatus provided with the sealed compressor 10 in any one of Embodiments 1-5, Embodiment 1 ~ Any one of the hermetic compressors 10 may be provided. For example, any one of Embodiments 1 to 5 may be applied to other equipment using a refrigeration cycle (heat pump cycle) such as an air conditioner, a vending machine, another refrigeration apparatus, and an industrial compressor such as an air compressor. The hermetic compressor 10 may be used.

(Other embodiments)
In all the above embodiments, the gaps between the front ends of the plate-like members 45 and 46 and the front side member 42 or between the rear ends of the plate-like members 45 and 46 and the rear side member 41 are openings. The parts 45a and 46a were provided. On the other hand, when the front end of each plate-like member 45, 46 reaches the front member 42, or when the rear end of each plate-like member 45, 46 reaches the rear member 41, each plate-like Holes penetrating the members 45 and 46 may be provided as the openings 45a and 46a.

  Also in this case, since the sound waves reflected by the plate-like members 45 and 46 and the sound waves that have passed through the openings 45a and 46a overlap each other so as to weaken, noise caused by high-frequency sound waves can be reduced. it can.

  In all the above embodiments, the first plate member 45 and the second plate member 46 are integrally formed with the rear member 41 or the front member 42. In contrast, the first plate member 45 and the second plate member 46 may be molded separately from the rear member 41 and the front member 42 and fixed to the rear member 41 or the front member 42. Thereby, the 1st plate-shaped member 45 and the 2nd plate-shaped member 46 can be fixed to the desired position of the rear member 41 or the front member 42. For example, the first plate member 45 may be fixed to the left side surface portions 41e and 42e, or the second plate member 46 may be fixed to the lower side surface portions 41c and 42c. At this time, the rear ends of the plate members 45 and 46 are separated from the rear main surface portion 41a, and the front ends of the plate members 45 and 46 are separated from the front main surface portion 42a. Thus, the openings 45a and 46a are located between the rear ends of the plate-like members 45 and 46 and the rear main surface portion 41a and between the front ends of the plate-like members 45 and 46 and the front main surface portion 42a. Is also formed.

  In all the above embodiments, the suction muffler 40 is divided in the front-rear direction, and is formed by integrating the rear member 41 and the front member 42. However, the suction muffler 40 may be formed by dividing the upper muffler 40 in the vertical direction and integrating the upper member and the lower member. In this case, when the first plate-like member 45 and the second plate-like member 46 are integrally formed with the lower member, either one of the plate-like members 45, 46 is connected to the second discharge port 44b that is the open end of the tail pipe. It is fixed to the front main surface portion or the rear main surface portion of the lower member in the vertical direction so as to face each other.

  In all the embodiments described above, the plate-like members 45 and 46 may be further provided in the expansion space for the suction muffler provided with the resonance chamber independent of the expansion space. In this case, the silencer space of the suction muffler is used as an expansion space and a resonance chamber provided independently of each other. The silence space corresponding to this expansion space is also used as a resonance space. Therefore, it is possible to mute a sound wave having a narrow specific frequency in the resonance chamber and reduce a high frequency sound wave in a wide range in the resonance space while reducing a low frequency sound wave in the expansion space.

  Note that all the above embodiments may be combined with each other as long as they do not exclude each other. From the foregoing description, many modifications and other embodiments of the present invention are apparent to persons skilled in the art. Accordingly, the foregoing description should be construed as illustrative only and is provided for the purpose of teaching those skilled in the art the best mode of carrying out the invention. The details of the structure and / or function may be substantially changed without departing from the spirit of the invention.

  The hermetic compressor and the refrigeration apparatus including the same of the present invention are useful as a hermetic compressor that improves the noise reduction effect and a refrigeration apparatus including the hermetic compressor.

10: Sealed compressor 11: Sealed container 20: Compression element 22a: Cylinder (block)
23: Piston 30: Electric element 41: Rear member 45: First plate member (member, plate member)
46: Second plate member (member, plate member)
50: Refrigerator (freezer)

Claims (19)

An electric element;
A compression element driven by the electric element;
A sealed container that houses the electric element and the compression element,
The compression element includes a block in which a compression space is formed, a piston that is driven by the electric element and reciprocates in the compression space, and a suction space in which a sound deadening space that communicates with the compression space is formed. With a muffler,
The silence space is lower than the resonance frequency by enlarging the cross-sectional area of the resonance space that reduces the sound wave of the resonance frequency that matches the natural frequency of the sealed container by interference and the area of the communication port with the compression space. A hermetic compressor, further comprising a member that is also used as an expansion space for reducing frequency sound waves. A plate-like member is provided in the silencing space,
The plate-like member partitions the silencing space into a space on one main surface side of the plate-like member and a space on the other main surface side, and the space on the one main surface side and the other main surface side. The hermetic compressor according to claim 1, further comprising an opening that partially communicates with the space. An electric element;
A compression element driven by the electric element;
A sealed container that houses the electric element and the compression element,
The compression element includes a block in which a compression space is formed, a piston that is driven by the electric element and reciprocates in the compression space, and a suction space in which a sound deadening space that communicates with the compression space is formed. With a muffler,
A plate-like member is provided in the silencing space,
The plate-like member partitions the silencing space into a space on one main surface side of the plate-like member and a space on the other main surface side, and the space on the one main surface side and the other main surface side. A hermetic compressor having an opening partly communicating with the space.   The hermetic compressor according to claim 2 or 3, wherein a dimension of the plate-like member is 90% or less with respect to a dimension of the plate-like member and the opening.   The hermetic compressor according to any one of claims 2 to 4, wherein a dimension of the opening changes in a longitudinal direction of the plate member. The suction muffler further includes a communication pipe that communicates the silencing space and the compression space;
The plate member includes a first plate member,
6. The suction port of the communication pipe is disposed at or near the middle between the first plate-like member and the inner surface of the suction muffler facing the first plate-like member. The hermetic compressor according to claim 1. The inhalation muffler further includes a tail pipe that communicates the silencing space and the sealed container;
The plate member includes a second plate member,
The discharge port of the tail pipe is disposed in the middle or in the vicinity between the second plate-like member and the inner surface of the suction muffler facing the second plate-like member. The hermetic compressor according to claim 1. The suction muffler further includes a communication pipe that communicates the silencing space and the compression space, and a tail pipe that communicates the silencing space and the sealed container,
The plate member includes a first plate member and a second plate member,
An inlet port of the communication pipe is disposed in the middle or in the vicinity between the first plate-like member and the inner surface of the suction muffler facing the first plate-like member,
The discharge port of the tail pipe is disposed in the middle or in the vicinity between the second plate-like member and the inner surface of the suction muffler facing the second plate-like member. The hermetic compressor according to claim 1. The inhalation muffler has a first surface portion that faces the sealed container, and a second surface portion that faces the first surface portion,
The hermetic compressor according to claim 8, wherein both the first plate-like member and the second plate-like member are provided so as to protrude from the inner surface of the first surface portion or the second surface portion. The inhalation muffler has a first surface portion that faces the sealed container, and a second surface portion that faces the first surface portion,
The first plate-like member is provided to protrude from the inner surface of one of the first surface portion and the second surface portion, and the second plate-like member is provided to protrude from the inner surface of the other surface portion. The hermetic compressor according to claim 8. The inhalation muffler has a third surface portion where the tail pipe is formed, and a fourth surface portion facing the third surface portion,
The hermetic compressor according to claim 8, wherein both the first plate-like member and the second plate-like member are provided so as to protrude from the inner surface of the third surface portion or the fourth surface portion. The inhalation muffler has a third surface portion where the tail pipe is formed, and a fourth surface portion facing the third surface portion,
The first plate member is provided to protrude from the inner surface of one of the third surface portion and the fourth surface portion, and the second plate member is provided to protrude from the inner surface of the other surface portion. The hermetic compressor according to claim 8.   The hermetic compressor according to any one of claims 8 to 12, wherein the first plate-like member and the second plate-like member are provided in directions orthogonal to each other.   The hermetic compressor according to any one of claims 8 to 12, wherein the first plate-like member and the second plate-like member are provided in directions parallel to each other. The compression element further includes a tail pipe that communicates the silencing space and the sealed container;
The hermetic compressor according to any one of claims 2 to 14, wherein the plate-like member extends in front of the discharge port from a discharge port of the tail pipe in a longitudinal direction thereof. The inhalation muffler has a bottom surface;
The hermetic compressor according to any one of claims 2 to 15, wherein a gap is provided between a lower end of the plate-like member extending in the vertical direction and the lower surface portion.   The hermetic compressor according to any one of claims 2 to 16, wherein the piston is disposed above the electric element.   The hermetic compressor according to any one of claims 2 to 17, wherein the electric element is driven at a plurality of rotation speeds by an inverter drive circuit.   A refrigeration apparatus comprising the hermetic compressor according to any one of claims 1 to 18.