JP2006183660A - Compressor and refrigerating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor whose height is reduced by improving storage efficiency in a compartment. <P>SOLUTION: A rotor recessed part 111a is provided to a compression element 113 side of a rotor 111. A bearing part 135 is extended in the rotor recessed part 111a. An inverter-driven motor operated at multiple rotational speeds is taken as an electromotive element 110. A permanent magnet 151 is used for the rotor 111 to reduce the height of the compressor. An abutting surface of a leg of the compressor and the elastic member is positioned above the lower end surface of the supporting member, thereby reducing the overall height of the compressor. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a compressor and a refrigeration apparatus using the compressor.

  Hereinafter, a refrigerator to which the conventional compressor is applied will be described with reference to the drawings.

  Conventional refrigerators generally have a machine room disposed at the lower rear of the refrigerator body, and house high-pressure components of a refrigeration cycle such as a compressor in the machine room. In recent years, refrigerators have become easier to use. From the standpoints of goodness and space saving, improved storage properties and from the viewpoint of the global environment are demanded to improve energy savings. The method of installing in the surface or the back upper part of a refrigerator main body is proposed (for example, refer patent document 1).

  FIG. 33 shows the configuration of a refrigerator to which the conventional compressor described in Patent Document 1 is applied.

  The box body 1 of the refrigerator is composed of a refrigerator compartment 2, a vegetable compartment 3, and a freezer compartment 4 from the top. The refrigerator compartment 2 has a refrigerating compartment rotary door 5, and the vegetable compartment 3 has a vegetable compartment drawer door 6, a freezer compartment. The chamber 4 has a freezer compartment drawer door 7.

  The cooling unit 10 including the internal fan 8 and the evaporator 9 has a rear surface of the freezer compartment 4 that is substantially the same height as the opening of the freezer compartment 4 that forms a storage portion as the lowermost storage compartment. It is installed in the rear part, and is installed in the recessed part 12 which is a machine room recessed in the refrigerator compartment 2 side over the top surface 11a and the back surface 11b of the box body 1 of the refrigerator which is not convenient to use the compressor 11.

  The refrigerator compartment 2 is provided with a plurality of shelves 12b for storing food and the like, and the box main body 1 extends between the uppermost storage space 12c and the second storage space 12d partitioned by the uppermost shelf 12b. The recessed part 12 provided in the back upper part of is traveling as a convex part 12e.

In such a configuration, as the compressor 11 moves, the freezer compartment 4 and the vegetable compartment 3 are reduced in height by the storage volume of the compressor 11, so that the partition wall that partitions the refrigerator compartment 2 and the vegetable compartment 3 The position can be lowered downward, and the stored items in the vegetable room 3 can be easily taken out.
JP-A-11-183014

  However, in the above-described conventional configuration, the convex portion 12e formed on the inner side corresponding to the concave portion 12 which is a machine room has a poor design and the storage property is reduced. Therefore, in order to make the convex portion 12e as small as possible, The recessed part 12 needs to be lowered, and there is a problem of reducing the height of the compressor 11, which is the maximum factor for determining the height of the recessed part 12.

  This is not limited to the type of refrigerator having the above-described conventional configuration in which the compressor is disposed at the top, but is the same as long as it is a type of refrigerator that has a large restriction with respect to the height direction of the machine room storing the compressor. The problem arises.

  The present invention solves the above-described conventional problems, and provides a compressor mounted on a refrigerator that can improve the storage efficiency in the warehouse and can realize these without impairing the reliability of the compressor. For the purpose.

  In order to solve the above problems, a compressor according to the present invention houses an electric element composed of a stator and a rotor and a compression element driven by the electric element in a sealed container, and the sealed container contains the electric element. The compressor leg is fixed, and the compressor leg is elastically supported via an elastic member with respect to the installation surface of the compressor, and the mechanical part composed of the compression element and the electric element is attached to a sealed container. The compression element is elastically supported via a support member, and the compression element includes a compression chamber, a piston that reciprocates in the compression chamber, a shaft having a main shaft portion and an eccentric portion. The rotor fixed to the main shaft portion, and a bearing portion that pivotally supports the main shaft portion, and a rotor recess on the compression element side of the rotor, A bearing portion extends into the rotor recess, and the electric element is A motor of an inverter that is operated at a number of rotations, and a permanent magnet is used for the rotor of the electric element, thereby reducing the height of the mechanical part, and the legs of the compressor and the elastic member; The height of the compressor is reduced by positioning the contact surface above the lower end surface of the support member.

  As a result, the height of the machine room for storing the compressor can be reduced, the storage space in the warehouse can be widened, and the storage performance can be greatly improved.

  In addition, the vibration amplitude of the compressor is such that the entire compressor vibrates around the center of gravity where the vibration near the center of gravity is the smallest and the vibration increases as the distance from the center of gravity increases. Since the vibration amplitude of the contact surface between the leg closer to the center of gravity and the elastic member is smaller than vibration, vibration transmission to the refrigerator can be further reduced, and unpleasant vibration and noise caused by vibration are generated. It is possible to provide a high-quality compressor without the above.

  The compressor according to the present invention can reduce the protrusion of the machine room, which is a compressor storage space provided in the refrigerator, to the inner side of the machine room, has a good appearance inside the refrigerator, and is mounted on the refrigerator with improved storage properties. A machine can be provided.

  According to a first aspect of the present invention, an electric element composed of a stator and a rotor and a compression element driven by the electric element are accommodated in a hermetic container, and the hermetic container includes a compressor. The leg of the compressor is elastically supported via an elastic member with respect to the installation surface of the compressor, and the mechanical part composed of the compression element and the electric element is supported with respect to the sealed container. The compression element is elastically supported via a member, and the compression element includes a compression chamber, a piston that reciprocates in the compression chamber, a shaft having a main shaft portion and an eccentric portion, and a reciprocating type. The rotor fixed to the main shaft portion, and a bearing portion that pivotally supports the main shaft portion, and a rotor concave portion on the compression element side of the rotor, and the bearing portion Extending into the rotor recess, the electric element is rotated at a plurality of rotational speeds. By using a permanent magnet for the rotor of the electric element, the height of the mechanical part is reduced, and the contact surface between the leg of the compressor and the elastic member is provided. The height of the compressor is reduced by being positioned above the lower end surface of the support member.

  As a result, the height of the machine room for storing the compressor can be reduced, the storage space in the warehouse can be widened, and the storage performance can be greatly improved.

  Further, as a result, the vibration of the compressor is transmitted downward through the support member from the mechanical part which is a vibration generation source, and then the direction is changed upward and transmitted to the elastic member through the leg part. Therefore, since the vibration transmission path becomes complicated, the vibration is further attenuated in the transmission path, and further, the distance from the support member to the contact surface between the leg of the compressor and the elastic member can be increased. The vibration transmission in the high area is attenuated, and the amplitude of the vibration of the contact surface between the leg and the elastic member is reduced. Further, vibration transmission to the refrigerator can be reduced, resulting in unpleasant vibration or vibration. A high-quality refrigerator that does not generate noise can be provided.

  The amplitude of the vibration of the compressor is less than the vibration of the lower surface of the support member that supports the machine part because the entire compressor vibrates around the center of gravity where the vicinity of the center of gravity is the smallest and the vibration increases as it moves away from the center of gravity. Since the vibration amplitude of the contact surface between the leg closer to the center of gravity and the elastic member becomes smaller, vibration transmission to the refrigerator can be further reduced, and there is no unpleasant vibration or generation of noise caused by vibration. A high-quality compressor can be provided.

  According to a second aspect of the present invention, in the first aspect of the present invention, the distance between the center of gravity of the compressor in the vertical direction and the contact surface between the leg of the compressor and the elastic member is the compressor. Is shorter than the distance between the center of gravity in the vertical direction and the lower end surface of the support member.

  As a result, the amplitude of the vibration of the compressor is less than the vibration of the lower surface of the support member that supports the mechanical unit, because the entire compressor vibrates around the center of gravity where the vibration near the center of gravity is the smallest and increases as the distance from the center of gravity increases. However, since the vibration amplitude of the contact surface between the leg closer to the center of gravity and the elastic member becomes smaller, vibration transmission to the refrigerator can be further reduced, and there is no unpleasant vibration or generation of noise due to vibration. A high-quality compressor can be provided.

  The invention according to claim 3 of the present invention is the invention according to claim 1 or 2, wherein the height of the elastic member is set between the installation surface of the compressor in the recess and the lowermost part of the compressor. It is larger than the distance.

  As a result, it becomes a bulge in the refrigerator cabinet, which impairs the design and storage properties, and is effective for reducing vibration transmission from the compressor while reducing the height of the recess for storing the compressor. Since the height of the elastic member can be increased and the vibration can be further attenuated, it is possible to provide a high-quality refrigerator by reducing unpleasant vibration and generation of noise caused by the vibration.

  The invention according to claim 4 of the present invention is the invention according to any one of claims 1 to 3, wherein the legs of the compressor include a fixing surface that is fixed to the sealed container, a bending portion that rises upward, And a contact surface for locking the elastic member.

  As a result, the leg is positioned on the fixed surface of the lower part of the closed container with good workability such as joining, and the surface on which the elastic member is arranged should be a contact surface closer to the center of gravity. It can be formed by and is very easy to manufacture.

  Further, by forming the bent portion, it is possible to increase the distance from the surface where the leg is fixed to the sealed container to the lower surface where the elastic member is disposed, and the distance of vibration transmission from the surface is increased. In particular, transmission in a high frequency region is attenuated, and vibration transmission to the refrigerator can be reduced. Therefore, it is easy to manufacture and vibration transmission to the refrigerator can be reduced, and providing a high-quality compressor with less generation of unpleasant vibration and noise caused by vibration can be achieved at low cost.

  According to a fifth aspect of the invention, in the invention of the fourth aspect, the legs of the compressor are provided with ribs extending across at least two places of the fixing surface, the bending portion, and the contact surface. is there. As a result, the rigidity of the leg increases, the eigenvalue of the leg itself increases, and the leg itself hardly vibrates, so that the elastic member placement bottom surface of the leg, the elastic member, the refrigerator main body, Vibration transmission can be further reduced. Further, the rib can be formed by a press that is easy to manufacture, and the strength of the leg is increased. Therefore, another problem that is caused when the leg is deformed by the transport impact of the refrigerator can be improved.

  Therefore, it is easy to manufacture and vibration transmission to the refrigerator can be reduced, and providing a high-quality compressor with less generation of unpleasant vibration and noise caused by vibration can be achieved at low cost.

  The invention according to claim 6 is the invention according to any one of claims 1 to 5, wherein the electric element is wound via a plurality of salient pole part insulators of the stator core constituting the stator. Is a salient pole concentrated winding type.

  As a result, the winding does not cross between the distant slots, and the winding is concentrated densely on each salient pole portion, so that the winding does not rise due to the winding crossing between the slots, and compression is performed. The height of the electric elements of the machine can be further reduced, the overall height of the compressor can be further reduced, and the height of the recess where the compressor is installed can be reduced, improving the storage capacity of the lower stage of the refrigerator. In addition, the protrusion (projection) of the concave portion toward the storage space in the storage space can be reduced to improve the appearance, the storage space in the storage space can be widened, and the storage performance can be greatly improved.

  The invention according to claim 7 is the invention according to claim 6, wherein the compression element includes a cylinder block having a compression chamber, and the cylinder block includes a leg portion that forms a mounting surface to the electric element, The leg portion of the cylinder block is attached to the salient pole concentrated winding type stator core to shorten the length of the block leg portion.

  As a result, in a motor using salient pole concentrated winding, the coil end height, which is the height at which the winding protrudes from the stator core, can be made significantly lower than the coil end height of the winding of the induction motor. Therefore, the length of the leg portion of the cylinder block of the compression element can be greatly reduced, and the center of gravity of the compressor can be lowered further downward.

  According to an eighth aspect of the present invention, in the invention according to any one of the first to seventh aspects, the permanent magnet housed in the rotor is made of a rare earth permanent magnet.

  As a result, the rare-earth magnet has a magnetic flux density that is about four times larger than that of a commonly used ferrite magnet, so that even if the height of the magnet is lowered, the same or higher magnetic flux can be obtained. The height of the electric element can be further reduced, the overall height of the compressor can be further reduced, and the height of the recessed portion in which the compressor is installed can be reduced, so that the lower storability of the refrigerator is improved. At the same time, the protrusion (projection) of the concave portion toward the storage space in the storage space can be reduced to improve the appearance, the storage space in the storage space can be widened, and the storage performance can be greatly improved.

  The invention according to claim 9 is the invention according to any one of claims 1 to 8, wherein the height from the lower end of the sealed container to the top of the sealed container is 144 mm or less.

  Accordingly, it is possible to provide a compressor that can be mounted after realizing low vibration and low noise even in a refrigerator of a type having a restriction in the height direction of the machine room.

  A refrigeration apparatus according to a tenth aspect includes a refrigeration cycle in which the compressor, the condenser, the decompressor, and the evaporator according to any one of the first to ninth aspects are sequentially provided to form a series of refrigerant flow paths. I have it.

  As a result, it is possible to reduce the height of the machine room of the refrigeration system by reducing the noise and vibration, while ensuring the reliability of the compressor and reducing the noise and vibration. In the above, a highly reliable refrigeration apparatus with low noise and vibration can be provided.

  Embodiments of a compressor according to the present invention will be described below with reference to the drawings. The present invention is not limited to the embodiments.

(Embodiment 1)
1 is a longitudinal sectional view of a compressor according to the present embodiment, FIG. 2 is a horizontal sectional view of the compressor according to the present embodiment, and FIG. 3 is an induction motor of the compressor of the refrigerator according to the first embodiment. FIG. 4 is a plan view of the salient pole concentrated winding stator of the refrigerator compressor according to the embodiment. FIG. 5 is a perspective view of a leg portion of the compressor of the refrigerator in the same embodiment.

  In the figure, a mortar-shaped lower container 101 formed by deep drawing of a rolled steel plate having a thickness of 2 to 4 mm is engaged with an inverted mortar-shaped upper container 102, and the engagement portion is sealed by welding all around. A container 103 is formed, and a refrigerant 104 made of hydrocarbon R600a and a refrigerating machine oil 105 made of mineral oil having a high compatibility with R600a are stored in the sealed container 103 inside. A leg 106 is fixed to the lower side of the airtight container 103, and a hole 109 of the elastic member 107 is loosely connected to a pin 108 provided in the recess 27 of the refrigerator via an elastic member 107 locked to the leg 106. The position is fixed by fitting.

  Further, the leg 106 is elastically supported in the hermetic container 103 via a support portion 113a as a support member and a spring 114, and the vertical center of gravity A of the compressor 11, the leg 106 of the compressor, the elastic member 107, and the like. The distance B with the contact surface 106a is shorter than the distance C between the vertical center of gravity A of the compressor 11 and the lower end surface 113b of the support member.

  As in the present embodiment, when the center of gravity A in the height direction of the compressor is above the contact surface 106a between the leg 106 of the compressor and the elastic member 107, a support member inside the compressor The contact surface 106a between the leg 106 of the compressor and the elastic member 107 is located above the lower end surface 113b of the compressor.

  Moreover, the height of the elastic member 107 is made larger than the distance F between the installation surface D in the concave portion of the compressor and the lowest end E of the compressor.

  The leg 106 has a fixing surface 106b that is fixed to the closed container, a bent portion 106c that rises upward, and an elastic member arrangement lower surface 106d that locks the elastic member. The fixing surface 106b, the bent portion 106c, and the elastic member arrangement lower surface 106d. Ribs 106e extending across at least two of them are provided.

  The electric element 110 includes a rotor 111 and a salient pole concentrated winding stator 112. The compression element 113 is constructed above the electric element 110 and is driven by the electric element 110.

  The electric element 110 and the compression element 113 are both housed in the hermetic container 103 and elastically supported on the bottom of the lower container 101 and the lower end of the stator 112 via a support part 113a as a support member and a spring 114.

  A support portion 113a and a spring 114 provided at the lower end of the stator 112 are support members that elastically support the mechanical portion.

  A terminal 115 constituting a part of the lower container 101 is for communicating electricity (not shown) inside and outside the sealed container 103, and supplies electricity to the electric element 110 through a lead wire 116. Further, the sealed container 103 has a discharge tube 120 for connection to the discharge pipe 31 of the refrigeration system, a suction tube 121 for connection to the suction pipe 33, and a refrigerant 104 enclosed in the refrigeration system, and then the system is closed. A sealing tube 122 is provided.

  By the operation of the compression element 113, the refrigerant 104 is sucked into the sealed container 103 through the suction pipe 33 and the suction tube 121 and discharged from the discharge tube 120 to the discharge pipe 31.

  The discharge pipe 31 elastically connects the compression element 113 and the discharge tube 120 of the sealed container.

  Next, details of the compression element 113 will be described below.

  The shaft 130 has a main shaft portion 131 in which the rotor 111 is fixed by press-fitting or shrink fitting, and an eccentric portion 132 formed by being eccentric with respect to the main shaft portion 131. The cylinder block 133 has a substantially cylindrical compression chamber 134 and a bearing portion 135 for supporting the main shaft portion 131 of the shaft 130, and is formed above the electric element 110.

  At this time, a rotor recess 111a is formed on the compression element side of the rotor 111, and a bearing portion 135 extends into the rotor recess 111a.

  The piston 136 is loosely fitted in the compression chamber 134 and connected to the eccentric portion 132 of the shaft 130 by the connecting means 137, and the rotational motion of the shaft 130 is converted into the reciprocating motion of the piston 136. The refrigerant 104 in the sealed container 103 is sucked from the suction port 141 of the suction muffler 140 by enlarging and reducing the pressure, and is formed in the cylinder block 133 via a valve (not shown) provided in the cylinder head 142. The discharged muffler 143, the discharge pipe 144, and the discharge tube 120 are discharged to the discharge pipe 31 outside the sealed container 103.

  The discharge pipe 144, which is a high-pressure pipe, is a steel pipe having an inner diameter of 1.5 mm to 3.0 mm, and is formed so as to be flexible by using L-shaped or U-shaped bending. The tube 120 is connected with elasticity.

  Next, details of the electric element 110 will be described below.

  The rotor 111 includes a main body 150 in which silicon steel plates of 0.2 mm to 0.5 mm are stacked, a hole 152 that houses the permanent magnet 151 provided in the main body 150, and an end plate that closes the hole 152 after inserting the permanent magnet 151. 153 and is integrally fixed by caulking pins 154.

  The stator 112 includes a stator core 161 in which silicon steel plates having a thickness of 0.2 mm to 0.5 mm are stacked, and a winding 162 that is a copper wire having an insulation coating of 0.3 mm to 1 mm. The stator core 161 is a salient pole concentrated winding type in which salient pole portions 171 are formed in an annular shape at predetermined intervals, and a winding 162 is wound around the salient pole portion 171. Each winding is connected to one by a connecting line 172.

  Next, the inverter motor and the induction motor will be compared and described.

  For easy understanding, FIG. 6 shows a comparison of the cross section of the induction motor on the left side and the cross section of the inverter motor on the right side with the center line as a boundary. Each electric motor is used for a compressor having approximately the same maximum refrigerating capacity. The height L1 of the stator core 161 of the stator 112 of the inverter motor is significantly lower than the height H1 of the stator core 181 of the stator 180 of the induction motor. The height L4 of the rotor 111 of the inverter motor is also lower than the height H4 of the rotor 182 of the induction motor. Further, in the inverter motor using salient pole concentrated windings, the coil end height at which the winding 162 protrudes from the stator core 161, and L2 and L3 are H2 of the coil end height of the winding 183 of the induction motor. , Much lower than H3. Further, by using a rare earth magnet as the permanent magnet 151, the height L5 of the permanent magnet 151, the height L1 of the stator iron core 161 of the inverter motor, and the height L4 of the rotor 111 can be further reduced.

  Next, the operation of the compressor 11 will be described.

  When the compressor 11 is energized, electricity is supplied to the stator 112 of the electric element 110 through the terminal 115 and the lead wire 116, and the rotor 111 is rotated by the rotating magnetic field generated by the stator 112. Due to the rotation of the rotor 111, the eccentric portion 132 of the shaft 130 connected to the rotor performs a rotational motion that is eccentric from the axis of the shaft 130. The eccentric motion of the shaft 130 is converted into a reciprocating motion by the connecting means 137 connected to the eccentric portion 132 and becomes a reciprocating motion of the piston 136 connected to the other end of the connecting means 137, and the piston 136 is compressed into the compression chamber 134. The refrigerant 104 is sucked and compressed while changing the internal volume.

  The capacity of the piston 136 that is sucked and discharged during one reciprocation in the compression chamber 134 is referred to as a cylinder volume, and the ability to cool the cylinder volume changes.

  The compressor 11 supported by the elastic member 107 and the legs 106 that perform the above-described operation is mounted in a machine room (not shown) that is a recess formed on the back surface of the refrigerator, and the depth of the recess ( (Height) is determined by the height of the compressor 11.

  On the other hand, a convex portion corresponding to the concave portion makes a business trip in the refrigerator. When the convex portion is large, the storage property is deteriorated, so that a technique for reducing the height of the compressor 11 is required.

  The height of the compressor 11 will be specifically described. The compressor 11 uses steel plates of 2 to 4 mm for the lower container 101 and the upper container 102, and the total is about 7 mm. The lower container 101 and the upper container 102 each have a shape with a curvature in the vertical direction. This is because a specification with low noise is desired to make the living space where the refrigerator is installed comfortable. By giving the container a curvature, the rigidity and eigenvalue of the container are increased, and noise due to resonance is suppressed. The curvature is approximately R100 mm to R150 mm in radius, and in order to obtain this curvature, a little over 13 mm is required on one side.

  Next, refrigerating machine oil 105 is stored at the bottom of the sealed container 103. The refrigerating machine oil 105 is sealed in an amount of about 200 to 250 ml in order to guarantee the operation of the compressor 11 under various conditions, and occupies about 20 mm in height. Further, when the refrigerating machine oil 105 and the electric element 110 come into contact with each other, an abnormal increase in input occurs, so that a spatial distance of about 9 mm is necessary to prevent contact.

  Since it is more important to reduce the noise of the compressor 11 as well as to reduce the size of the compressor 11 mounted on the refrigerator for home use, it is important to improve the rigidity of the sealed container 103. From the viewpoint of improving reliability. It is also important to secure the refrigerating machine oil 105. For these reasons, the plate thickness is 7 mm, the curvature is 13 mm, the curvature and the oil are 20 mm, and 9 mm necessary for securing the clearance is required to be 49 mm. It is not appropriate in terms of characteristics to reduce this dimension.

  Therefore, the height of the compressor 11 is largely determined by the electric element 110 and the compression element 113. The compression element 113 can make the piston 136, the connecting means 137, the shaft 130, and the bearing part 135 compact by reducing the cylinder volume. For example, when R134a, which is generally used in the past, is used, Compared with the case of using R600a, the cylinder volume can be reduced to about ½ in order to obtain the same refrigeration capacity.

  Thus, although it is a compressor for R600a having a relatively large cylinder volume compared to the case of using R134a, which is disadvantageous from the viewpoint of miniaturization, in order to ensure the same refrigeration capacity, the compressor The cylinder volume of the refrigerant can be increased to about twice, thereby increasing the volume flow rate of the refrigerant and increasing the flow velocity in the pipe when the compressor is operating, so that the refrigerant flowing in the pipe when the compressor is operating By increasing the volume flow rate of the compressor, it is possible to secure a sufficient flow rate for the refrigeration oil to rise and rise up the piping, and to improve the reliability of the compressor by increasing the return amount of the refrigeration oil from the evaporator to the compressor can do.

  Moreover, the use of mineral oil as the refrigerating machine oil increases the solubility of the refrigerant in the refrigerating machine oil as compared with the conventional combination of R134a and ester oil.

  In this way, by using mineral oil, which is a refrigerating machine oil that is highly compatible with the R600a refrigerant, the solubility of the refrigerant in the refrigerating machine oil is increased compared to the conventional combination of R134a and ester oil. In addition, the reliability of the compressor can be further improved by using the thermosyphon effect to increase the return amount of the refrigerating machine oil from the evaporator to the compressor together with the refrigerant.

  Next, as shown on the left side of the center line in FIG. 6, the electric element 110 has an torque required for the operation of the compressor 11 unless the thicknesses H1 and H4 of the stator 180 and the rotor 182 are large. Does not occur. On the other hand, the use of an inverter motor using permanent magnets 151 for the rotor 111 eliminates the need for an excitation current necessary for generating rotational torque, so the stack thickness L1 of the stator 112 and the stack thickness of the rotor 111 are eliminated. L4 can be lowered, and the electric element 110 can be made compact. More specifically, the induction motor has to pass a current to the rotor side (secondary side), and in order to obtain this exciting current, a high thickness is required. Since there is a magnet, no exciting current is required to generate torque, and the thickness can be reduced.

  Furthermore, the dimension of the winding 162 of the stator 112 of the electric element 110 protruding from the stator core 161 is larger than the protruding dimensions H2 and H3 of the winding 183 in the distributed winding. Since it does not cross between distant slots and is concentrated and densely wound around each salient pole part, the winding does not rise due to the winding crossing between the slots, and as shown in L2 and L3 The overall height of the stator 112 is reduced, and the electric element 110 can be made more compact.

  In this manner, the projecting dimension of the windings from the iron core of the stator is reduced, so that the electric element 110 is reduced in size, and the cylinder block 133 which is a compression element is connected to the salient pole concentrated winding type stator core 161. The height of the leg 133a for attaching to the can be greatly shortened, and the compression element can be downsized at the same time.

  Furthermore, when a rare earth magnet is used for the permanent magnet 151 of the inverter motor, the magnetic properties are about 4 times that of a general ferrite magnet, and the energy product is about 10 times that of the magnetic product. Sufficient characteristics can be obtained. Therefore, the height L5 of the permanent magnet 151 and the height of the stator L1 can be further reduced, and the electric element 110 can be further compacted.

  Further, in the present embodiment, a rotor recess 111a is formed on the compression element 113 side of the rotor 111, and a bearing portion 135 extends into the rotor recess 111a. By arranging the electric element 110 and the compression element 113 so as to overlap each other on the projection surface in the height direction without shortening the length of the bearing part 135, the entire mechanical part including the electric element 110 and the compression element 113 can be obtained. The height can be greatly reduced, and the height of the compressor can be further reduced without reducing the reliability of the compressor.

  More specifically, in the design of the inventor, in the induction motor, the stack thickness of the stator 180 is 42 mm, the coil end heights H2 and H3 of the winding 183 are 25 mm, and the height H4 of the rotor 182 is 65 mm. On the other hand, in the inverter motor, when the stator L has a stack thickness L1 of 26 mm, and a rare earth magnet is used, the lower L1 is 16 mm, and the coil end heights L2 and L3 of the winding 162 of the stator 112 are When salient pole concentrated winding is used, L2 and L3 are 9 mm. Further, the rotor 111 has a thickness of 35 mm and can be reduced to 20 mm when a rare earth magnet is used, and can be reduced by a maximum of 58 mm compared to a compressor using an induction motor.

  Further, as described above, the rotor recess 111a is formed on the compression element 113 side of the rotor 111 at a depth of more than half of the height of the rotor, and the bearing portion 135 is formed in the rotor recess 111a. Since the extension of the rotor 111 is 35 mm and the rare earth magnet is used, the height of the machine part can be further reduced to about 10 mm, which is the extension of the bearing part 135. Therefore, the height of the entire machine part can be reduced by about 25 mm in total.

  Thus, by extending the extension allowance of the bearing portion 135, the sliding length between the shaft 130 and the bearing portion 135 can be increased without increasing the overall height, and the compression load applied to the shaft 130 can be reduced. As a result, the reliability of the compressor can be improved.

  However, as the extension length of the bearing portion 135 is increased, the depth of the rotor recess 111a is increased, so that the fixing margin of the rotor 111 to the shaft 130 is shortened.

  In particular, in a compressor arranged such that the compression element 113 is at the upper part and the electric element 110 is located at the lower part as in the present embodiment, the rotor provided in the lower electric element 110 is a shaft. For example, an induction motor such as an induction motor that obtains a magnetic force by flowing current inside the rotor, such as an induction motor, uses the rotor 111 during operation. Since there is a possibility that the heat generation becomes large and the rotor 111 falls off the shaft 130 due to thermal expansion, it is impossible to greatly reduce the fixing margin of the rotor 111 to the shaft 130 due to reliability problems. According to the inventor's study, when the permanent magnet 151 is used, since the magnetic force is obtained by the permanent magnet without flowing the current inside the rotor 111, the heat generation is greatly increased. Has become fence, further as compared with induction motors, the weight by height lowered is lighter, it is possible to greatly shorten the sticking margin. For example, even if the fixing allowance is reduced to about 6 mm, which is 20% or less of the total height of the rotor, the fixing force is sufficient, and the rotor 111 is detached from the shaft 130 due to heat generated during operation, vibration or impact due to transportation, etc. The compression element is compatible with the improvement in reliability by taking a long sliding length between the shaft 130 and the bearing portion 135 and the securing of the fixing force between the rotor 111 and the shaft 130 without falling off. It is possible to reduce the overall height of the mechanical unit including the 113 and the electric element 110.

  In addition, since the fixing allowance of the rotor 111 is shortened, the oil supply capability by an oil supply mechanism (not shown) provided inside the shaft 130 can be improved. This is a lift in which the distance between the bearing portion 135 and the lowermost sliding end of the shaft 130 and the refrigerating machine oil 105 is raised to the spiral groove for refueling the shaft 130, and this lift is significantly shortened. Because. As a result, the oil supply capability to the sliding portion between the shaft 130 and the bearing portion 135, the sliding portion of the compression element 113 via the shaft 130, and the like can be improved, thereby improving the reliability.

  In particular, when the compressor 11 is operated at a lower speed by mounting the inverter motor as in the present embodiment, the improvement in the oil supply capability is obtained by increasing the centrifugal force of the shaft in proportion to the decrease in the rotational speed. However, even if the compressor 11 is operated at a lower speed, the refrigerating machine oil to the sliding portion is improved by improving the oil supply capacity. 105 can be stably supplied.

  As described above, in order to achieve the downsizing in the height direction while simultaneously preventing the rotor 111 from falling off and improving the oil supply reliability, a permanent magnet is used for the rotor 111 having a total height of 35 mm, As a result of an experiment for confirming the oil supply amount by changing the fixing margin between the rotor 111 and the shaft 130 at the number of revolutions, the fixing margin between the rotor 111 and the shaft 130 is 80% of the total rotor height. When 50% is set, the oil supply amount is improved by about 3%, and a certain effect for improving the oil supply amount starts to be obtained. When it is further set to 30%, the oil supply amount is improved by about 5%, and in the case of 15%. On the other hand, the amount of oil supply was improved to about 8%.

  Furthermore, in order to confirm the improvement of the oil supply reliability at the time of the low rotation by the inverter compressor, as a result of the confirmation experiment of the oil supply amount at 20HZ, the fixing allowance between the rotor 111 and the shaft 130 is 80% of the total height of the rotor. Compared to the above case, when 50%, the oil supply amount is improved by about 5%, and a certain effect for improving the oil supply amount starts to be obtained, and when it is further 30%, the oil supply amount is improved by about 10%. However, in the case of 15%, the amount of oil supply was improved to about 15%.

  In this way, by extending the bearing into the rotor, the lift for raising the refrigerating machine oil 105 to the spiral groove for refueling is shortened, improving the refueling reliability, and during normal rotation and low rotation When both are set to 50% or less, an effect starts to be obtained, and when the content is desirably set to 30% or less, a certain effect margin is obtained. Further, when the fixing allowance is further shortened and reduced to about 15%, the effect is further enhanced, but there is a case where the influence of reliability of the rotor holding starts to appear, and it is necessary to sufficiently confirm the adoption. Therefore, it is desirable that the adhering allowance should not be less than 15% as much as possible, and if it is 10% or less, the reliability of holding the rotor is greatly lowered and should be avoided.

  In particular, at the time of low rotation, shortening the head for raising the refrigerating machine oil 105 to the spiral groove for oil supply is very effective for improving the oil supply amount. In recent years, energy saving of refrigerators has been promoted, and operation of a compressor with low rotation that is effective for energy saving is becoming mainstream. However, at this low speed, the amount of oil supply inevitably decreases, so that various improvements have been made in the oil supply structure inside the compressor to improve the amount of oil supply. The focus of improving the oil supply amount by shortening the cost is a technology that has multiple beneficial effects such as reducing the overall height of the compressor and lowering the center of gravity, as well as improving the oil supply amount at low rotation .

  As described above, the electric element 110 of the compressor 11 is an inverter-driven electric motor that is operated at a plurality of rotation speeds including at least a frequency higher than the commercial power supply frequency so that the overall height of the compressor 11 becomes lower. By using the permanent magnet 151 for the rotor 111, the compressor 11 can be made smaller, and the height of the recess 27, which is the machine room in which the compressor 11 is installed, can be made smaller. The protrusion of the convex portion 30b can be reduced to improve the appearance, the storage space in the warehouse can be widened, and the storage performance can be greatly improved.

  Further, a salient pole concentrated winding type in which a plurality of salient pole portions 171 of a stator iron core 161 constituting the stator 112 of the compressor 11 are wound with a winding 162 via an insulator, or a rare earth element is provided on the permanent magnet 151. The compressor 11 can be further reduced by using a magnet.

  On the other hand, in the compressor 11 of the present embodiment, in particular, the compression element 113 employs a reciprocating type including a compression chamber 134 and a piston 136 that reciprocates within the compression chamber 134. The compression element 113 and the electric element 110 are elastically supported via a spring 114.

  As described above, by reducing the height of the compressor 11 with elements other than the support structure portion of the compression element 113 and the electric element 110, the vibration can be reduced as compared with a rotary compressor or the like. In addition, the height of the compressor can be reduced even if it is a reciprocating compressor that has limitations in application to the refrigerator with the compressor upper arrangement type, especially the compressor. When 11 is arranged at the upper part, it becomes possible to reduce vibrations which are a major problem, so even in the compressor upper arrangement type refrigerator where there is a concern that vibrations are transmitted to the box body 1, the user's discomfort It is possible to provide a user-friendly refrigerator in which the height of the concave portion 27 in which the compressor 11 is installed is reduced while the storage capacity of the refrigerator is improved.

  The reciprocating compressor is an internal low-pressure type, and the electric element 110 is disposed below the sealed container 103 and supports the sealed container 103 via a support portion 113a and a spring 114. It is elastically supported, and the compression element 113 is disposed on the electric element 110 and connected to the sealed container 103 via a discharge pipe 144 that is a high-pressure pipe having an elastic shape. Since the compression element 113 that is a vibration source of the compressor is disposed via the electric element portion 110 with respect to the support member in the hermetic container 103, the compression element 113 is more elastic than the case where the compression element 113 is directly elastically supported. The distance from the support portion can be further increased, and the vibration generated in the compression element 113 is attenuated when passing through the stator of the electric element 110 having high rigidity, and then the support portion of the compressor. For transmitting from outside the compressor, it is possible to reduce the vibration of the compressor.

  Further, since the discharge pipe 144 which is a high-pressure pipe in the compression element 113 has an elastic shape, the vibration of the compression element 113 is attenuated by the discharge pipe 144 and transmitted to the outside of the compressor. Can be further reduced.

  Further, the leg 106 is elastically supported in the hermetic container 103 via a support portion 113a as a support member and a spring 114, and the vertical center of gravity A of the compressor, the leg 106 of the compressor, and the elastic member 107 are The distance B with the abutment surface 106a is shorter than the distance C between the center of gravity A in the vertical direction of the compressor and the lower end surface 113b of the support member, so that the vibration amplitude of the compressor is near the center of gravity A. Since the whole compressor vibrates around the center of gravity where the vibration is the smallest and the vibration increases as it moves away from the center of gravity, the contact surface between the leg 106 and the elastic member 107 closer to the center of gravity than the lower surface of the support member that supports the mechanical unit. Since the amplitude of vibration becomes small, vibration transmission to the refrigerator can be further reduced.

  Moreover, the permanent magnet 151 is used for the rotor 111, the height of the rotor 111 is made low, and the height of the stator 112 is made low by making the stator 112 into a salient pole concentrated winding type. The overall center of gravity can be lowered.

  Further, when the stator 112 is distributed winding, since the winding protrudes upward from the attachment portion of the cylinder block 133 to the stator 112, the dimension of the leg of the cylinder block 133 is larger than the protruding dimension of the winding. However, if the stator 112 is a salient pole concentrated winding type, it is possible to shorten the leg of the cylinder block 133 that is the attachment portion of the cylinder block 133 to the stator 112, and the compression element The center of gravity can also be lowered.

  Further, by extending the extension allowance of the bearing portion 135 of the cylinder block 133 to the rotor recess 111a, the cylinder block 133 can be lowered further and the center of gravity can be lowered.

  As described above, the center of gravity A of the mechanical portion inside the compressor is lowered, and the contact surface 106 between the leg 106 and the elastic member 107 provided in the sealed container 103 outside the compressor is positioned further upward. By doing so, the distance B between the center of gravity A, the contact surface of the leg 106 and the elastic member 107 is further reduced, and vibration transmission from the compressor to the refrigerator can be further reduced.

  This is particularly important in a target where both low vibration and low noise are indispensable, while miniaturization of the overall height of the compressor such as a refrigerator of the type in which the compressor is arranged at the top is required. While various elements for reducing the size of the compressor are conceivable, in terms of internal configuration, the permanent magnet 151 is used for the rotor 111, while maintaining the retaining effect of the rotor 111 by the shaft 130. The bearing portion 135 is further extended into the rotor to reduce the internal height, and on the external configuration surface, the mounting surface of the leg 106 on the elastic member 107 is raised, so that the total height is maintained even when installed in the refrigerator. Therefore, it is possible to achieve a low-vibration compact compressor having a low center of gravity and high support stability.

  Further, according to the present embodiment, the contact surface 106a between the leg of the compressor and the elastic member is located above the lower end surface 113b of the support member, whereby the vibration of the compressor generates vibration. After being transmitted downward through the support member from the mechanical part as the source, the direction changes upward and is transmitted to the elastic member 107 via the leg 106. Therefore, since the vibration transmission path becomes complicated, the vibration is further attenuated in the transmission path, and further, the distance from the support member to the contact surface 106a between the leg 106 of the compressor and the elastic member 107 can be increased. In particular, the vibration transmission in a high frequency region is attenuated, and the amplitude of vibration of the contact surface 106a between the leg 106 and the elastic member 107 is reduced. Further, vibration transmission to the refrigerator can be reduced, and unpleasant vibration or It is possible to provide a high-quality refrigerator that does not generate noise due to vibration.

  Further, the leg 106 has a fixing surface 106b that is fixed to the sealed container 103, a bent portion 106c that rises upward, and an elastic member disposing lower surface 106d that locks the elastic member. It is located on the fixed surface 106b of the lower portion of the closed container 103, and the surface on which the elastic member is arranged can be the elastic member arrangement lower surface closer to the center of gravity, by forming the bent portion by simple leg bending, It is very easy to manufacture.

  Further, the fixing surface 106b fixed to the closed container 103 of the leg 106 is below the lower end surface 113b that is the fixing surface of the support member 113a of the lower container 101, and the vibration of the compression element 113 that is the vibration source of the compressor. Is transmitted to the fixing surface of the support member 113a located farthest from the excitation source in the sealed container 103 through the electric element 110 and also through the spring 114 supported by the support member 113a. So the vibration is greatly damped.

  Further, the leg 106 extends from the fixing surface in a substantially horizontal direction, rises vertically upward by the formation of the bent portion 106c, and bends in the substantially horizontal direction again, and then the elastic member disposition lower surface 106d is formed. The vibration transmission path becomes complicated and long up to the contact surface 106a with the member 107, and the vibration transmission is attenuated. Further, the elastic member 107 has a lower elastic member arrangement lower surface 106d closer to the center of gravity A in the vertical direction of the compressor, and the elastic member 107 has a sufficient length. Therefore, vibration transmission to the refrigerator can be sufficiently reduced, and a high-quality refrigerator free from unpleasant vibration and noise caused by vibration can be provided.

  In the present embodiment, the vertical rising height is 24 mm. This is about 16% of the total height of the compressor.

  The vertical rising height is above the lower end surface 113b of the support portion 113a, but the lower end portion of the spring 114 engaged with the support portion 113a is fitted to the support portion 113a. Therefore, since it is fixed to the airtight container without having elasticity, it is more desirable to be above the lower end portion of the spring having elasticity with respect to the airtight container.

  Also, as the vertical rise height increases, the distance of the rising portion becomes longer, so it becomes difficult to obtain high rigidity at the rising portion. In such a case, a vibration phenomenon occurs in which the vertical direction is twisted back and forth around the contact surface 106a between the leg 106 and the elastic member 107, and stress concentration occurs around the rising portion of the leg 106. In view of the external impact force, it is considered desirable for the reliability of the compressor to be about 30% or less with respect to the total height of the compressor.

  Further, the formation of the bent portion 106c makes it possible to increase the distance from the surface where the leg 106 is fixed to the sealed container 103 to the lower surface where the elastic member 107 is disposed, and transmission of vibration from the fixing surface 106b. Since the distance becomes long, transmission in a particularly high frequency region is attenuated, and vibration transmission to the refrigerator can be reduced. Therefore, manufacture is easy and vibration transmission to the refrigerator can be reduced, and providing a high-quality refrigerator free from unpleasant vibration and noise generation due to vibration can be achieved at low cost.

  Furthermore, by providing the leg 106 with the rib 106e extending over the bent portion 106c and the elastic member arrangement lower surface 106d, the rigidity of the leg 106 is increased, the eigenvalue of the leg 106 itself is increased, and the leg 106 itself vibrates. Therefore, it is possible to further reduce vibration transmission from the fixing surface of the sealed container 103 to the elastic member and the refrigerator main body through the legs. Further, the rib can be formed by a press that is easy to manufacture, and the strength of the leg is increased. Therefore, another problem that the leg is deformed by the transport impact of the refrigerator can be improved.

  Therefore, manufacture is easy and vibration transmission to the refrigerator can be reduced, and providing a high-quality refrigerator free from unpleasant vibration and noise generation due to vibration can be achieved at low cost.

  As described above, the downsizing element in the height direction of the compressor 11 can be broadly distinguished from the viewpoint corresponding to the electric element 110 and the viewpoint corresponding to the compression element 113. Whether to keep it in any one of the elements may be selected based on a balance between a required value for height reduction and other characteristics and quality.

  For example, a method of mainly configuring a height reduction element that is combined with the electric element 110 that does not require relatively high-precision durability and reliability and is not likely to cause significant noise and vibration is a configuration in which the compressor 11 is disposed above. Is advantageous in that it can be downsized while suppressing the effects on noise and vibration.

  On the other hand, when trying to achieve the purpose by downsizing the compression element 113, it is possible to expect a reduction in size by reducing the cost, which is advantageous in terms of cost performance.

  In addition, as described above, the compressor 11 is arranged on the upper part of the box body 1 of the refrigerator so that it is closer to the user's ear, so that it is necessary to consider noise and vibration more than the conventional refrigerator, and the compression Miniaturization by reducing the height of the machine 11 is important in combination with miniaturization elements that do not affect the noise and vibration of the refrigerator, and the structure for supporting the electric element 110 and the compression element 113 and the sealed container 103 are provided. It is also effective to incorporate ingenuity to reduce the height while suppressing noise and vibration in the supporting structure, or to not incorporate a simple height reduction design that adversely affects noise and vibration.

(Embodiment 2)
FIG. 6 is a schematic cross-sectional view of the compressor of the refrigerator in the second embodiment of the present invention.

  FIG. 7 is a schematic cross-sectional view of the refrigerator compressor according to Embodiment 2 of the present invention.

  In addition, although configurations and operational effects common to the first embodiment will not be described one by one, it is assumed that the same contents are included unless they are unreasonable when applied to the present embodiment.

  In the drawing, the compression element 209 includes a main bearing 220 and a sub-shaft portion 210c, which are bearing portions that support the main shaft portion 210b, the sub-shaft portion 210c, and the main shaft portion 210b coaxially with the eccentric portion 210a of the shaft 210 interposed therebetween. The auxiliary bearing 221 that supports the shaft is provided.

  In addition, the eccentric portion 210 a is provided with a piston 232 that reciprocates in the compression chamber 231 via the connecting member 230.

  Further, as shown in the figure, the sealed container 250 includes an upper container 251 and a lower container 252, and a plurality of legs 260 fixed to the lower container 252 are installed in the recess through the elastic member 270, and the compression of the recess is performed. The machine installation surface 280 is provided with a recess 281 and an elastic member 270 is provided in the recess 281 so that the height of the elastic member 270 is larger than the distance between the compressor installation surface 280 and the lowest part 290 of the compressor. It is equipped with a compressor. Further, the lower side of the elastic member 270 is fitted and fixed in the recess 281.

  The operation and action of the compressor configured as described above will be described below.

  Since the refrigerant is compressed to a high pressure in the compression chamber 231 while the compressor is in operation, this compression load is transmitted to the eccentric portion 210 a via the piston 232 and the connecting member 230.

  When the compressive load received by the eccentric portion of the shaft 210 is transmitted to the entire shaft 210, a large surface pressure is applied to the sliding portion between the main shaft portion 210b of the shaft and the main bearing 220.

  This surface pressure increases as the sliding length between the main shaft portion 210b of the shaft 210 and the main bearing 220 becomes shorter. In this embodiment, in addition to the main shaft portion 210b of the shaft 210 and the main bearing 220, the surface pressure increases. Since the shaft 210 is pivotally supported at two locations, that is, the minor shaft portion 210c of the shaft 210 and the subsidiary bearing 221 that pivotally supports the shaft 210, the piston 232 as a vibration source can be supported from both sides, and the shaft can be further bent. And the reliability of the sliding surface of the shaft 210 can be improved.

  Further, even if the sliding length of the main bearing 220 is shortened compared to the conventional case, the sliding length of the entire shaft 210 can be secured by complementing the sliding length of the auxiliary bearing 221, so that the reliability of the compressor The height of the compressor can be further reduced without lowering the performance.

  Therefore, in the reciprocating compressor, the piston 232 that reciprocates according to the present invention is provided for securing the bearing length that supports the shaft 210, which is one of the major problems in reducing the height. Since the main bearing 220 and the auxiliary bearing 221 are provided on both sides of the eccentric portion 210a, the piston 232 as a vibration source can be supported from both sides, and the shaft 210 can be prevented from being bent and the shaft can slide. Since the reliability of the surface can be improved, the reliability of the compressor can be ensured even if the sliding length of the main bearing is shorter than the conventional one, so that the reliability of the compressor is not lowered. The height of the compressor can be further reduced.

  In this embodiment, the auxiliary bearing 221 is provided on the opposite side of the main bearing 220 with the eccentric portion 210a interposed therebetween. However, even if the auxiliary shaft portion is provided coaxially with the main shaft portion 210b with the rotor 240 interposed therebetween, Similarly, the bearing length for supporting the shaft 210 can be ensured, and the reliability of the compressor can be ensured even if the sliding length of the main bearing is shorter than the conventional one. The height of the compressor can be further reduced without lowering.

  In addition, a recess 281 is provided on the compressor installation surface 280 of the recess, and the elastic member 270 is disposed in the recess 281 so that the height of the elastic member 270 is set to the compressor installation surface. By becoming larger than the distance of 280 and the lowest part 290 of a compressor, the height of the elastic member 270 effective in order to transmit the vibration from the compressor to a refrigerator can be made high. On the other hand, the wall thickness of the installation surface is a factor that determines the size of the convex part into the refrigerator compartment, but a certain amount of thickness is necessary as a structure that supports the compressor in order to obtain the cooling characteristics of the refrigerator. However, with the formation of the recess, it is possible to reduce vibration transmission by increasing the height of the elastic member, ensure cooling characteristics by ensuring the thickness of the installation surface, and ensure the strength as a structure that supports the compressor. Since the height of the elastic member effective for transmitting the vibration from the compressor can be increased, unpleasant vibration and noise generation due to the vibration can be greatly reduced, and the refrigerator Therefore, it is possible to maintain the characteristics by securing the heat insulating property of the steel and to maintain the transport resistance by securing the strength of the structure, and to provide a high-quality refrigerator.

  In this way, by reducing the vibration by increasing the height of the elastic member by forming a recess as an external support structure that supports the compressor, the reliability of the compressor is reduced while further reducing the height of the compressor Without causing the noise, the unpleasant vibration caused by the compressor and the noise generation caused by the vibration can be greatly reduced, and the convex part inside the refrigerator of the type in which the compressor is mounted on the top of the refrigerator Can be reduced in size.

  In addition, by fitting and fixing the lower side of the elastic member, it is possible to fix the position of the elastic member without adding extra parts, eliminating the displacement of the compressor, and transmitting vibrations due to changes in the support surface of the elastic member. It is possible to reduce the change, and to provide a high-quality refrigerator that greatly reduces the generation of unpleasant vibration on the refrigerator installation surface of the elastic member and the noise caused by the vibration, while being inexpensive and improving transport resistance.

(Embodiment 3)
FIG. 8 is a schematic cross-sectional view of a compressor according to Embodiment 3 of the present invention. FIG. 9 is a schematic perspective view of a sealed container of the compressor according to Embodiment 3 of the present invention. FIG. 10 is a schematic plan view of a sealed container of the compressor according to Embodiment 3 of the present invention. FIG. 11 is a schematic cross-sectional view of the compressor in the present embodiment.

  In addition, the configuration and operational effects common to the first and second embodiments will not be described one by one. However, the same contents are included unless they are unreasonable when applied to the present embodiment. In the present embodiment, a description will be given of the sealed container of the compressor described in the first and second embodiments.

  In the figure, a plurality of bumps 410 are provided at the bottom of the sealed container 403.

  The plurality of bump portions 410 are mainly convex convex portions that are convex from the inside of the sealed container to the outside, and concave shapes that are concave from the outside of the sealed container 403 to the inside. And a concave bump 411.

  As the convex bump portion, a leg bump portion 410 a is provided in the vicinity of the connecting portion 420 between the compressor leg 406 and the closed vessel 403 provided in the closed vessel 403. The leg-cove portion 410a is a convex cove portion in which the periphery of the connection portion 420 is formed with a curvature that is clearly smaller than the curvature of the outer periphery of the sealed container.

  In addition, the support member 413 that supports the mechanical part including the electric element and the compression element inside the sealed container includes a support part 413 a that is a support member and a spring 414 that is an elastic member, and is hermetically sealed at the lower end surface of the support part 413. A support bump 410b is provided in the vicinity of the container. The support bump portion 410b is a convex bump portion having a vertically lower periphery of the support portion formed with a curvature that is clearly smaller than the curvature of the outer periphery of the sealed container.

  Further, the sealed container 403, the leg 406, and the support part 413a below the spring 414 are fixed by spot welding, that is, the leg 406 and the lower end part of the support part 413 are welded to the convex hump part.

  Further, the closed container is formed with a concave bump 411 that is recessed inwardly from the outer periphery of the closed container, and is formed with a curvature that is clearly smaller than the curvature of the outer periphery of the closed container. It is formed continuously.

  The operation and action of the compressor configured as described above will be described below.

  As in the present embodiment, by providing a plurality of bumps 410 especially in the lower part of the sealed container 403, the top and bottom surfaces of the sealed container are placed, for example, from the center of the compressor in order to reduce the height direction of the compressor. It becomes difficult to provide a substantially spherical curved surface, and there is a tendency that the upper surface and the lower surface of the sealed container have a curved surface close to a flat surface.

  Thus, if there is a flat curved surface that is close to a flat surface in the shape of the sealed container 403, the rigidity of the portion is weakened and it is easy to be affected by noise and vibration.

  Therefore, in the present embodiment, the support bump portion 410b is provided in the vicinity of the hermetic container located at the lower end surface of the support part 413 of the mechanical part that is a vibration source and the hermetic container. By providing a support bump portion 410b having a small curvature in the vicinity of the connecting portion 420 as a fixing surface between the lower end of the support portion 413a and the closed vessel 403 when propagating to the closed vessel via the spring 414. Since the rigidity in the vicinity of the lower end portion of the support portion can be improved, vibration and noise transmitted from the compressor to the sealed container can be reduced.

  Furthermore, by providing a leg cove portion 410a in the vicinity of the connecting portion 420 between the compressor leg 406 and the sealed container 403, which is the external support of the compressor on the lower surface side of the sealed container, such as the sealed container 403, Since the rigidity in the vicinity of the connection portion 420 can be improved, vibration and noise that propagate from the sealed container to the refrigerator main body via the legs 406 can be reduced.

  In this way, a curved surface having a large curvature such that the lower surface side of the hermetic container is close to a flat surface in order to reduce the overall height of the compressor by providing a bump-like convex part in the vicinity of the support part on the inner side and the outer side of the compressor. Even in such a case, a refrigerator with reduced vibration and noise can be provided by using a compressor in which the rigidity of the sealed container, particularly in the vibration transmission path, is improved.

  Further, in the present embodiment, the concave bump portion 411 is formed continuously in the closed container, and the concave portion having a small curvature is continuously formed in a complicated shape. By doing so, there is an effect of further improving the rigidity of the hump portion.

  Further, in addition to the hump portion having a small curvature centering on the vibration transmission path of the sealed container 403 as in the present embodiment, the compressor leg and the elastic member as described in the first embodiment are provided. If the type in which the contact surface 106a is positioned above the lower end surface 113b of the support member is used, the vibration of the compressor is supported downward from the mechanical part that is the source of vibration. After transmitting through the member, the direction changes upward and the rigidity of the transmission path when transmitting to the elastic member 107 via the legs 106 can be further increased and the transmission path can be complicated, so the vibration of the refrigerator can be reduced. It can be further reduced.

  Furthermore, since the elastic member 107 has a lower surface 106d of the elastic member closer to the center of gravity A in the vertical direction of the compressor, the amplitude of the vibration of the compressor is the smallest in the vicinity of the center of gravity A and vibrates with increasing distance from the center of gravity. Since the entire compressor vibrates around the center of gravity so that the vibration is large, the vibration amplitude of the contact surface between the leg 106 and the elastic member 107 closer to the center of gravity is smaller than the lower surface of the support member that supports the mechanical unit. Furthermore, vibration transmission to the refrigerator can be reduced.

  Further, in addition to the hump portion having a small curvature centering on the vibration transmission path of the sealed container 403 as in the present embodiment, the concave portion of the compressor installation surface 280 as described in the second embodiment is provided. Is provided with a depression 281 and an elastic member 270 is disposed in the depression 281 so that the height of the elastic member 270 is larger than the distance between the compressor installation surface 280 and the lowermost part 290 of the compressor. In addition to the effect of reducing vibration transmission from the machine part to the leg part of the compressor, the elastic member can be made larger, and the vibration and noise of the refrigerator can be further reduced.

  Further, in addition to the hump portion having a small curvature centering on the vibration transmission path of the sealed container 403 as in the present embodiment, the hump portion is provided with a fixing surface 456a of the leg portion as shown in FIG. In the case, even when the bent portion that rises upward from the fixing surface as described in the first embodiment is not provided, if the fixing portion of the leg portion to the sealed container is a hump portion, Since it is possible to reduce the vibration in the vibration transmission path of the compressor, even when the bent portion that rises upward from the fixing portion with the sealed container is not necessarily provided, the contact between the compressor leg 456 and the elastic member 457 is not necessary. Since the contact portion 458 can be disposed at a portion closer to the center of gravity A in the vertical direction of the compressor, the vibration amplitude of the compressor is the smallest in the vicinity of the center of gravity A and becomes larger as the distance from the center of gravity increases. Since the entire compressor vibrates around the center of gravity, the amplitude of vibration of the contact surface 458 between the leg 456 and the elastic member 457 closer to the center of gravity is smaller than the lower surface of the support member that supports the mechanical unit. Vibration transmission to can be reduced.

  Therefore, it is possible to provide a compressor that is easy to manufacture and can reduce vibration transmission to the refrigerator, and it is low-cost to provide a high-quality refrigerator that is free from unpleasant vibration and noise caused by vibration. Can be achieved.

(Embodiment 4)
12 is a schematic cross-sectional view of the refrigerator according to Embodiment 4 of the present invention, FIG. 13 is a schematic rear view of the refrigerator according to the embodiment, and FIG. 14 is a schematic exploded view of components of the refrigerator according to the embodiment. 15 is a longitudinal sectional view of the compressor of the refrigerator in the embodiment, FIG. 16 is a horizontal sectional view of the compressor of the refrigerator in the embodiment, and FIG. 17 is an induction of the compressor of the refrigerator in the embodiment. FIG. 18 is a plan view of a salient pole concentrated winding stator of the refrigerator compressor in the embodiment. FIG. 19 is a perspective view of a leg portion of the compressor of the refrigerator in the same embodiment.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, about the same structure as background art, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

  In the figure, the box body 1 injects a foam insulator 15 into a space formed by an inner box 13 formed by vacuum forming a resin body such as ABS and an outer box 14 using a metal material such as a pre-coated steel plate. It has a heat insulation wall. As the heat insulator 15, for example, a hard urethane foam, a phenol foam, a styrene foam, or the like is used. As the foam material, it is better to use hydrocarbon-based cyclopentane from the viewpoint of preventing global warming.

  The box body 1 is divided into a plurality of heat insulating sections, and a door 15a is provided on the front surface. The door 15a is configured such that the upper part is a revolving door type and the lower part is a drawer type. The heat-insulated storage room 15b is a refrigerator room 2, a drawer-type switching room 16 and an ice making room 17, a drawer-type vegetable room 3, and a drawer-type freezer room 4 provided side by side. Each heat insulation section is provided with a door 15 a having heat insulation properties via a gasket 18. From the top are the refrigerating room rotary door 5, the switching room drawer door 19, the ice making room drawer door 20, the vegetable room drawer door 6, and the freezer compartment drawer door 7.

  The refrigerator compartment revolving door 5 is provided with a door pocket 21 as a storage space, and a plurality of storage shelves 22 are provided in the warehouse.

  Next, details of the box body 1 will be described. The outer box 14 of the box body 1 has a U-curved outer shell panel 24 cut out from the top surface 23, a bottom panel 25, a back panel 26, and a machine room panel 28 that forms a recess 27 to ensure sealing performance. And is constructed by assembling. The assembled box body 1 has a recess 27 formed in a portion extending over the top surface 23 and the back surface 28a. The concave portion 27 is convex on the uppermost storage space 29a defined by the uppermost shelf 29 and the inner box 13 and the second shelf storage space 30a defined by the second shelf 30 and the uppermost shelf 29. I am on a business trip as 30b. More preferably, the indoor side bottom wall surface 30c of the convex portion 30b and the shelf bottom portion 30d of the uppermost shelf 29 are substantially the same horizontal plane.

  In addition, the bottom panel 25 and the back panel 26 are provided with handles made of depressions that can be hooked with fingertips.

  Further, the inner box 13 is slightly smaller than the outer box 14, and the back portion of the inner box 13 is recessed inward, and a space in which the heat insulating body 15 is foam-filled by being incorporated in the outer box 14 is a box body. 1 is formed. Therefore, the left and right parts of the machine room panel 28 are also filled with the heat insulator 15 to form heat insulating walls, and the strength is also ensured.

  Next, the refrigeration cycle will be described. In the refrigeration cycle, the compressor 11 disposed on the installation surface 28 b of the recess 27, the discharge pipe 31 connected to the compressor 11, the top surface 23 and the side surface of the outer shell panel 24, the condensation provided on the recess 27 and the bottom panel 25. A vacuum chamber (not shown), a capillary 32 as a decompressor, a dryer (not shown) for removing moisture, an evaporator 9 having an internal fan 8 disposed in the vicinity of the back of the vegetable compartment 3 and the freezing compartment 4 The suction pipe 33 is connected in a ring shape.

  The recess 27 is provided with a top cover 34 fixed with screws or the like. The compressor 11 and the machine room fan 34a, the condenser (not shown), and the dryer (not shown) provided in the recess 27 are provided. A part of the discharge pipe 31 and the suction pipe 33 are accommodated. The upper portion of the top cover 34 is substantially flush with the top surface 23, and the top 34 b of the compressor 11 is located at a position lower than the top surface 23.

  The capillary 32 and the suction pipe 33 are copper pipes having substantially the same length, and are soldered so as to allow heat exchange with the end portion remaining. The capillary 32 is a small-diameter steel pipe having a large internal flow resistance for decompression. The inner diameter of the capillary 32 is about 0.6 mm to 1.0 mm, and the amount of decompression is designed by adjusting with the length. The suction pipe 33 uses a large-diameter copper pipe to reduce pressure loss, and its inner diameter is about 6 mm to 8 mm. Further, the capillary 32 and the suction pipe 33 are arranged in a compact manner by meandering the back surface of the refrigerator 2 in order to ensure the length of the heat exchanger section 35, and are located between the inner box 13 and the back panel 26. It is embedded in the heat insulator 15. One end of the capillary 32 and the suction pipe 33 protrudes from the vicinity of the rear of the vegetable compartment 3 of the inner box 13 and is connected to the evaporator 9, and the other end is connected to the edge of the installation surface 28 b of the machine room panel 28. It protrudes upward from the provided cutout and is connected to a dryer (not shown), a condenser (not shown), and the compressor 11.

  In addition, the suction pipe 33 and the discharge pipe 31 are provided with a U-turn portion 36 in the vicinity of the connection portion with the compressor 11 for providing connection flexibility, and are accommodated in the recess 27. Furthermore, with the aim of improving assembly workability and serviceability, in order to reduce the density of piping and to make the piping connection portion visible from the rear, the piping connection portion faces the back side of the compressor 11. Thus, the compressor 11 is arranged on the left and right sides of the compressor 11.

  Next, details of the compressor 11 will be described.

  In the figure, a mortar-shaped lower container 101 formed by deep drawing of a rolled steel plate having a thickness of 2 to 4 mm is engaged with an inverted mortar-shaped upper container 102, and the engagement portion is sealed by welding all around. A container 103 is formed, and inside the sealed container 103, refrigerant 104 and refrigerating machine oil 105 are stored at the bottom. A leg 106 is fixed to the lower side of the airtight container 103, and a hole 109 of the elastic member 107 is loosely connected to a pin 108 provided in the recess 27 of the refrigerator via an elastic member 107 locked to the leg 106. The position is fixed by fitting.

  In addition, the leg 106 is elastically supported in the sealed container 103 via a support portion 113a, which is a support member, and a spring 114. The distance B with the contact surface 106a is shorter than the distance C between the vertical center of gravity A of the compressor 11 and the lower end surface 113b of the support member.

  As in the present embodiment, when the center of gravity A in the height direction of the compressor is above the contact surface 106a between the leg 106 of the compressor and the elastic member 107, a support member inside the compressor The contact surface 106a between the leg 106 of the compressor and the elastic member 107 is located above the lower end surface 113b of the compressor.

  Moreover, the height of the elastic member 107 is made larger than the distance F between the installation surface D in the concave portion of the compressor and the lowest end E of the compressor.

  The leg 106 has a fixing surface 106b that is fixed to the closed container, a bent portion 106c that rises upward, and an elastic member arrangement lower surface 106d that locks the elastic member. The fixing surface 106b, the bent portion 106c, and the elastic member arrangement lower surface 106d. Ribs 106e extending across at least two of them are provided.

  The electric element 110 includes a rotor 111 and a salient pole concentrated winding stator 112. The compression element 113 is constructed above the electric element 110 and is driven by the electric element 110.

  The electric element 110 and the compression element 113 are both housed in the hermetic container 103 and elastically supported on the bottom of the lower container 101 and the lower end of the stator 112 via a support part 113a as a support member and a spring 114.

  A support portion 113a and a spring 114 provided at the lower end of the stator 112 are support members that elastically support the mechanical portion.

  A terminal 115 constituting a part of the lower container 101 is for communicating electricity (not shown) inside and outside the sealed container 103, and supplies electricity to the electric element 110 through a lead wire 116. Further, the sealed container 103 has a discharge tube 120 for connection to the discharge pipe 31 of the refrigeration system, a suction tube 121 for connection to the suction pipe 33, and a refrigerant 104 enclosed in the refrigeration system, and then the system is closed. A sealing tube 122 is provided.

  By the operation of the compression element 113, the refrigerant 104 is sucked into the sealed container 103 through the suction pipe 33 and the suction tube 121 and discharged from the discharge tube 120 to the discharge pipe 31.

  The discharge pipe 31 elastically connects the compression element 113 and the discharge tube 120 of the sealed container.

  Next, details of the compression element 113 will be described below.

  The shaft 130 has a main shaft portion 131 in which the rotor 111 is fixed by press-fitting or shrink fitting, and an eccentric portion 132 formed by being eccentric with respect to the main shaft portion 131. The cylinder block 133 has a substantially cylindrical compression chamber 134 and a bearing portion 135 for supporting the main shaft portion 131 of the shaft 130, and is formed above the electric element 110.

  At this time, a rotor recess 111a is formed on the compression element side of the rotor 111, and a bearing portion 135 extends into the rotor recess 111a.

  The piston 136 is loosely fitted in the compression chamber 134 and connected to the eccentric portion 132 of the shaft 130 by the connecting means 137, and the rotational motion of the shaft 130 is converted into the reciprocating motion of the piston 136. The refrigerant 104 in the sealed container 103 is sucked from the suction port 141 of the suction muffler 140 by enlarging and reducing the pressure, and is formed in the cylinder block 133 via a valve (not shown) provided in the cylinder head 142. The discharged muffler 143, the discharge pipe 144, and the discharge tube 120 are discharged to the discharge pipe 31 outside the sealed container 103.

  The discharge pipe 144, which is a high-pressure pipe, is a steel pipe having an inner diameter of 1.5 mm to 3.0 mm, and is formed so as to be flexible by using L-shaped or U-shaped bending. The tube 120 is connected with elasticity.

  Next, details of the electric element 110 will be described below.

  The rotor 111 includes a main body 150 in which silicon steel plates of 0.2 mm to 0.5 mm are stacked, a hole 152 that houses the permanent magnet 151 provided in the main body 150, and an end plate that closes the hole 152 after inserting the permanent magnet 151. 153 and is integrally fixed by caulking pins 154.

  The stator 112 includes a stator core 161 in which silicon steel plates having a thickness of 0.2 mm to 0.5 mm are stacked, and a winding 162 that is a copper wire having an insulation coating of 0.3 mm to 1 mm. The stator iron core 161 has salient pole portions 171 formed in an annular shape at a predetermined interval, and windings 162 are wound around the salient pole portions 171 (referred to as salient pole concentrated windings). They are connected together by a line 172.

  Next, the inverter motor and the induction motor will be compared and described.

  In order to make the explanation easy to understand, the cross section of the induction motor is compared with the cross section of the induction motor on the left side and the cross section of the inverter motor on the right side with the center line as a boundary. Each electric motor is used for a compressor having approximately the same maximum refrigerating capacity. The height L1 of the stator core 161 of the stator 112 of the inverter motor is significantly lower than the height H1 of the stator core 181 of the stator 180 of the induction motor. The height L4 of the rotor 111 of the inverter motor is also lower than the height H4 of the rotor 182 of the induction motor. Further, in the inverter motor using salient pole concentrated windings, the coil end height at which the winding 162 protrudes from the stator core 161, and L2 and L3 are H2 of the coil end height of the winding 183 of the induction motor. , Much lower than H3. Further, by using a rare earth magnet as the permanent magnet 151, the height L5 of the permanent magnet 151, the height L1 of the stator iron core 161 of the inverter motor, and the height L4 of the rotor 111 can be further reduced.

  About the refrigerator comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  First, the temperature setting of each heat insulation section will be described. The refrigerator compartment 2 is usually set at 1 to 5 ° C. with the lower limit of the temperature at which it does not freeze for refrigeration. The switching chamber 16 can be changed in temperature setting according to user settings, and can be set to a desired temperature range from the freezer temperature range to the refrigeration and vegetable room temperature ranges. The ice making chamber 17 is an independent ice storage chamber and is set at a relatively high temperature of -18 to -10 ° C.

  The vegetable room 3 is often set to 2 to 7 ° C., which is a temperature setting equal to or slightly higher than that of the refrigerator room 2. The freezer compartment 4 is usually set at −22 to −18 ° C. for frozen storage, but may be set at a lower temperature, for example, −30, in order to improve the storage state.

  Each chamber is divided by a heat insulating wall in order to efficiently maintain different temperature settings. The heat insulating wall is formed by foaming and filling the heat insulating body 15 between the inner box 13 and the outer box 14. . The heat insulator 15 has sufficient heat insulating performance and ensures the strength of the box body 1.

  Next, the operation of the refrigeration cycle will be described. The cooling operation is started and stopped by signals from a temperature sensor (not shown) and a control board (not shown) in accordance with the set temperature in the cabinet. In response to the instruction to start the cooling operation, the compressor 11 discharges the high-temperature and high-pressure refrigerant 104. The discharged refrigerant 104 passes through the discharge pipe 31 to dissipate heat in a condenser (not shown) to be condensed and liquefied, and is depressurized by the capillary 32 to become a low-temperature and low-pressure liquid refrigerant, reaches the evaporator 9, and reaches the evaporator 9. The refrigerant in the inside is evaporated and the low-temperature cold air subjected to heat exchange is distributed by a damper (not shown) to cool each chamber.

  Next, the operation of the compressor 11 will be described.

  When the compressor 11 is energized, electricity is supplied to the stator 112 of the electric element 110 through the terminal 115 and the lead wire 116, and the rotor 111 is rotated by the rotating magnetic field generated by the stator 112. Due to the rotation of the rotor 111, the eccentric portion 132 of the shaft 130 connected to the rotor performs a rotational motion that is eccentric from the axis of the shaft 130. The eccentric motion of the shaft 130 is converted into a reciprocating motion by the connecting means 137 connected to the eccentric portion 132 and becomes a reciprocating motion of the piston 136 connected to the other end of the connecting means 137, and the piston 136 is compressed into the compression chamber 134. The refrigerant 104 is sucked and compressed while changing the internal volume.

  The capacity of the piston 136 that is sucked and discharged during one reciprocation in the compression chamber 134 is referred to as a cylinder volume, and the ability to cool the cylinder volume changes.

  In the refrigerator that performs the operation as described above, the compressor 11 supported by the elastic member 107 and the legs 106 is mounted in a recess 27 formed across the top surface 23 and the back surface 28a of the refrigerator. The depth (height) of the recess is at least the minimum gap between the bottom of the lower container 101 of the compressor 11 and the installation surface 28b, the height of the compressor 11, and the minimum gap between the upper container 102 and the top cover 34, The thickness of the top cover 34 is necessary. In order to avoid contact between the compressor 11 and the installation surface 28b or the top surface cover 34, a minimum clearance is required, and the minimum thickness of the top surface cover 34 is determined from the strength surface. ) Is determined by the height of the compressor 11.

  On the other hand, the convex portion 30b is on a business trip by the concave portion 27 in the refrigerator. When the convex portion 30b is large, the storage property is deteriorated, and when the refrigerating chamber rotating door 5 is opened and the inside of the refrigerator compartment 2 is viewed, the appearance of the convex portion 30b is deteriorated. Therefore, a technique for reducing the height of the compressor 11 is required.

  The height of the compressor 11 will be specifically described. The compressor 11 uses steel plates of 2 to 4 mm for the lower container 101 and the upper container 102, and the total is about 7 mm. The lower container 101 and the upper container 102 each have a shape with a curvature in the vertical direction. This is because a specification with low noise is desired to make the living space where the refrigerator is installed comfortable. By giving the container a curvature, the rigidity and eigenvalue of the container are increased, and noise due to resonance is suppressed. The curvature is approximately R100 mm to R150 mm in radius, and in order to obtain this curvature, a little over 13 mm is required on one side.

  Next, refrigerating machine oil 105 is stored at the bottom of the sealed container 103. The refrigerating machine oil 105 is sealed in an amount of about 200 to 250 ml in order to guarantee the operation of the compressor 11 under various conditions, and occupies about 20 mm in height. Further, when the refrigerating machine oil 105 and the electric element 110 come into contact with each other, an abnormal increase in input occurs, so that a spatial distance of about 9 mm is necessary to prevent contact.

  In the refrigerator in which the compressor 11 is loaded on the top surface 23 of the refrigerator, since the compressor 11 approaches the position of the user's ear, it is more important to keep the noise of the compressor 11 small. Improvement is important, and securing the refrigerating machine oil 105 is also important from the viewpoint of improving reliability. For these reasons, the plate thickness is 7 mm, the curvature is 13 mm, the curvature and the oil are 20 mm, and 9 mm necessary for securing the clearance is required to be 49 mm. It is not appropriate in terms of characteristics to reduce this dimension.

  Therefore, the height of the compressor 11 is largely determined by the electric element 110 and the compression element 113. The compression element 113 can make the piston 136, the connecting means 137, the shaft 130, and the bearing portion 135 compact by reducing the cylinder volume. However, when the cylinder volume is reduced, the refrigerating capacity is reduced. In the present embodiment, in order to obtain a large capacity with a small cylinder volume, the compression element 113 is made compact by operating at a rotational speed higher than the commercial power supply frequency (50 Hz or 60 Hz in Japan). More specifically, since the cylinder volume can be reduced by about 30%, the diameter of the piston 136 can be reduced, and the load acting on the shaft 130 can be reduced. Therefore, the length of the bearing portion 135 that supports the shaft load is also reduced. Therefore, the electric element 110 can be configured close to the compression element 113. By making good use of the high rotation by the inverter, the inventor's design is able to make it 5 to 10 mm compact.

  The setting of the plurality of rotation speeds of the electric element 110 by the inverter method does not necessarily include a rotation speed corresponding to a frequency higher than the commercial power supply frequency (50 Hz or 60 Hz) in Japan.

  That is, a combination of settings that does not exceed the upper limit of a plurality of determined frequencies exceeding the commercial power supply frequency (not limited to Japan) is expected to save energy and reduce noise. There is also a combination that corresponds to the effect and does not dare to make the cylinder volume of the compression element 113 compact.

  Next, as shown on the left side of the center line in FIG. 6, the electric element 110 has an torque required for the operation of the compressor 11 unless the thicknesses H1 and H4 of the stator 180 and the rotor 182 are large. Does not occur. On the other hand, the use of an inverter motor using permanent magnets 151 for the rotor 111 eliminates the need for an excitation current necessary for generating rotational torque, so the stack thickness L1 of the stator 112 and the stack thickness of the rotor 111 are eliminated. L4 can be lowered, and the electric element 110 can be made compact. More specifically, the induction motor has to pass a current to the rotor side (secondary side), and in order to obtain this exciting current, a high thickness is required. Since there is a magnet, no exciting current is required to generate torque, and the thickness can be reduced.

  Furthermore, the dimension of the winding 162 of the stator 112 of the electric element 110 protruding from the stator core 161 is larger than the protruding dimensions H2 and H3 of the winding 183 in the distributed winding. Since it does not cross between distant slots and is concentrated and densely wound around each salient pole part, the winding does not rise due to the winding crossing between the slots, and as shown in L2 and L3 The overall height of the stator 112 is reduced, and the electric element 110 can be made more compact.

  Furthermore, when a rare earth magnet is used for the permanent magnet 151 of the inverter motor, the magnetic properties are about 4 times that of a general ferrite magnet, and the energy product is about 10 times that of the magnetic product. Sufficient characteristics can be obtained. Therefore, the height L5 of the permanent magnet 151 and the height of the stator L1 can be further reduced, and the electric element 110 can be further compacted.

  Further, in the present embodiment, a rotor recess 111a is formed on the compression element 113 side of the rotor 111, and a bearing portion 135 extends into the rotor recess 111a. By arranging the electric element 110 and the compression element 113 so as to overlap each other on the projection surface in the height direction without shortening the length of the bearing part 135, the entire mechanical part including the electric element 110 and the compression element 113 can be obtained. The height can be greatly reduced, and the height of the compressor can be further reduced without reducing the reliability of the compressor.

  More specifically, in the design of the inventor, in the induction motor, the stack thickness of the stator 180 is 42 mm, the coil end heights H2 and H3 of the winding 183 are 25 mm, and the height H4 of the rotor 182 is 65 mm. On the other hand, in the inverter motor, when the stator L has a stack thickness L1 of 26 mm, and a rare earth magnet is used, the lower L1 is 16 mm, and the coil end heights L2 and L3 of the winding 162 of the stator 112 are When salient pole concentrated winding is used, L2 and L3 are 9 mm. Further, the rotor 111 has a thickness of 35 mm and can be reduced to 20 mm when a rare earth magnet is used, and can be reduced by a maximum of 58 mm compared to a compressor using an induction motor.

  Further, as described above, the rotor recess 111a is formed on the compression element 113 side of the rotor 111 at a depth of more than half of the height of the rotor, and the bearing portion 135 is formed in the rotor recess 111a. Since the extension of the rotor 111 is 35 mm and the rare earth magnet is used, the height of the machine part can be further reduced to about 10 mm, which is the extension of the bearing part 135. Therefore, the height of the entire machine part can be reduced by about 25 mm in total.

  Thus, by extending the extension allowance of the bearing portion 135, the sliding length between the shaft 130 and the bearing portion 135 can be increased without increasing the overall height, and the compression load applied to the shaft 130 can be reduced. As a result, the reliability of the compressor can be improved.

  However, as the extension allowance is lengthened, the depth of the rotor recess 111a increases, so that the allowance for fixing the rotor 111 to the shaft 130 is shortened.

  In particular, in a compressor arranged such that the compression element 113 is at the upper part and the electric element 110 is located at the lower part as in the present embodiment, the rotor provided in the lower electric element 110 is a shaft. For example, an induction motor such as an induction motor that obtains a magnetic force by flowing current inside the rotor, such as an induction motor, uses the rotor 111 during operation. Since there is a possibility that the heat generation becomes large and the rotor 111 falls off the shaft 130 due to thermal expansion, it is impossible to greatly reduce the fixing margin of the rotor 111 to the shaft 130 due to reliability problems. According to the inventor's study, when the permanent magnet 151 is used, since the magnetic force is obtained by the permanent magnet without flowing the current inside the rotor 111, the heat generation is greatly increased. Has become fence, further as compared with induction motors, the weight by height lowered is lighter, it is possible to greatly shorten the sticking margin. For example, even if the fixing allowance is reduced to about 6 mm, which is 20% or less of the total height of the rotor, the fixing force is sufficient, and the rotor 111 is detached from the shaft 130 due to heat generated during operation, vibration or impact due to transportation, etc. The compression element is compatible with the improvement in reliability by taking a long sliding length between the shaft 130 and the bearing portion 135 and the securing of the fixing force between the rotor 111 and the shaft 130 without falling off. It is possible to reduce the overall height of the mechanical unit including the 113 and the electric element 110.

  In addition, since the fixing allowance of the rotor 111 is shortened, the oil supply capability by an oil supply mechanism (not shown) provided inside the shaft 130 can be improved. This is a lift in which the distance between the bearing portion 135 and the lowermost sliding end of the shaft 130 and the refrigerating machine oil 105 is raised to the spiral groove for refueling the shaft 130, and this lift is significantly shortened. Because. As a result, the oil supply capability to the sliding portion between the shaft 130 and the bearing portion 135, the sliding portion of the compression element 113 via the shaft 130, and the like can be improved, thereby improving the reliability.

  In particular, when the compressor 11 is operated at a lower speed by mounting the inverter motor as in the present embodiment, the improvement in the oil supply capability is obtained by increasing the centrifugal force of the shaft in proportion to the decrease in the rotational speed. However, even if the compressor 11 is operated at a lower speed, the refrigerating machine oil to the sliding portion is improved by improving the oil supply capacity. 105 can be stably supplied.

  As described above, in order to achieve the downsizing in the height direction while simultaneously preventing the rotor 111 from falling off and improving the oil supply reliability, a permanent magnet is used for the rotor 111 and the rotational speed is 50 Hz. As a result of an experiment for confirming the oil supply amount by changing the fixing margin between the rotor 111 and the shaft 130, the fixing margin between the rotor 111 and the shaft 130 is 50% compared to the case where the fixing margin is 80% of the total height of the rotor. In this case, the oil supply amount is improved by about 3%, and a certain effect for improving the oil supply amount starts to be obtained. When the oil supply amount is further set to 30%, the oil supply amount is improved by about 5%, and in the case of 15%, The amount of lubrication was improved to about 8%.

  Furthermore, in order to confirm the improvement of the oil supply reliability at the time of low rotation by the inverter compressor, as a result of an experiment for confirming the oil supply amount at 20 HZ, the fixing allowance between the rotor 111 and the shaft 130 is 80% of the total height of the rotor. Compared to the above case, when 50%, the oil supply amount is improved by about 5%, and a certain effect for improving the oil supply amount starts to be obtained, and when it is further 30%, the oil supply amount is improved by about 10%. However, in the case of 15%, the amount of oil supply was improved to about 15%.

  In this way, by extending the bearing into the rotor, the lift for raising the refrigerating machine oil 105 to the spiral groove for refueling is shortened, improving the refueling reliability, and during normal rotation and low rotation When both are set to 50% or less, an effect starts to be obtained, and when the content is desirably set to 30% or less, a certain effect margin is obtained. Further, when the fixing allowance is further shortened and reduced to about 15%, the effect is further enhanced, but there is a case where the influence of reliability of the rotor holding starts to appear, and it is necessary to sufficiently confirm the adoption. Therefore, it is desirable that the adhering allowance should not be less than 15% as much as possible, and if it is 10% or less, the reliability of holding the rotor is greatly lowered and should be avoided.

  In particular, at the time of low rotation, shortening the head for raising the refrigerating machine oil 105 to the spiral groove for oil supply is very effective for improving the oil supply amount. In recent years, energy saving of refrigerators has been promoted, and operation of a compressor with low rotation that is effective for energy saving is becoming mainstream. However, at this low speed, the amount of oil supply inevitably decreases, so that various improvements have been made in the oil supply structure inside the compressor to improve the amount of oil supply. The focus of improving the oil supply amount by shortening the cost is a technology that has multiple beneficial effects such as reducing the overall height of the compressor and lowering the center of gravity, as well as improving the oil supply amount at low rotation .

  As described above, the inverter drive that operates the electric element 110 of the compressor 11 at a plurality of rotation speeds including at least a frequency higher than the commercial power supply frequency so that the top of the compressor 11 is lower than the top surface 23 of the box body 1. By using the permanent magnet 151 for the rotor 111 of the electric element 110, the compressor 11 can be made smaller, and the height of the recess 27 in which the compressor 11 is installed can be reduced, so that the lower storability of the refrigerator is improved. In addition, the protrusion of the concave portion 27 toward the storage space in the storage space can be reduced to improve the appearance, the storage space in the storage space can be widened, and the storage performance can be greatly improved.

  Further, a salient pole concentrated winding type in which a plurality of salient pole portions 171 of a stator iron core 161 constituting the stator 112 of the compressor 11 are wound with a winding 162 via an insulator, or a rare earth element is provided on the permanent magnet 151. By using a magnet, the compressor 11 can be further reduced, and the height of the concave portion 27 in which the compressor 11 is installed can be reduced, so that the storage property of the lower stage of the refrigerator is improved and the concave portion 27 is moved to the storage space side in the cabinet. The protrusion of the convex portion 30b can be made small to improve the appearance, the storage space in the warehouse can be widened, and the storage performance can be greatly improved.

  On the other hand, in the compressor 11 of the present embodiment, in particular, the compression element 113 employs a reciprocating type including a compression chamber 134 and a piston 136 that reciprocates within the compression chamber 134. The compression element 113 and the electric element 110 are elastically supported via a spring 114.

  As described above, by reducing the height of the compressor 11 with elements other than the support structure portion of the compression element 113 and the electric element 110, the vibration can be reduced as compared with a rotary compressor or the like. In addition, the height of the compressor can be reduced even if it is a reciprocating compressor that has a limitation of application in a refrigerator with an upper arrangement type compressor. Since it becomes possible to reduce the vibration which becomes a big subject when arrange | positioning in the upper part, even if it is a compressor top arrangement type refrigerator with a possibility that a vibration may transmit to the box main body 1, removing a user's discomfort It is possible to provide an easy-to-use refrigerator in which the height of the concave portion 27 in which the compressor 11 is installed is reduced and the storage property of the lower stage of the refrigerator is improved.

  The reciprocating compressor is an internal low-pressure type, and the electric element 110 is disposed below the sealed container 103 and supports the sealed container 103 via a support portion 113a and a spring 114. It is elastically supported, and the compression element 113 is disposed on the electric element 110 and connected to the sealed container 103 via a discharge pipe 144 that is a high-pressure pipe having an elastic shape. Since the compression element 113 that is a vibration source of the compressor is disposed via the electric element portion 110 with respect to the support member in the hermetic container 103, the compression element 113 is more elastic than the case where the compression element 113 is directly elastically supported. The distance from the support portion can be further increased, and the vibration generated in the compression element 113 is attenuated when passing through the stator of the electric element 110 having high rigidity, and then the support portion of the compressor. For transmitting from outside the compressor, it is possible to reduce the vibration of the compressor.

  Further, since the discharge pipe 144 which is a high-pressure pipe in the compression element 113 has an elastic shape, the vibration of the compression element 113 is attenuated by the discharge pipe 144 and transmitted to the outside of the compressor. Can be further reduced.

  Further, the leg 106 is elastically supported in the hermetic container 103 via a support portion 113a as a support member and a spring 114, and the vertical center of gravity A of the compressor, the leg 106 of the compressor, and the elastic member 107 are The distance B with the abutment surface 106a is shorter than the distance C between the center of gravity A in the vertical direction of the compressor and the lower end surface 113b of the support member, so that the vibration amplitude of the compressor is near the center of gravity A. Since the whole compressor vibrates around the center of gravity where the vibration is the smallest and the vibration increases as it moves away from the center of gravity, the contact surface between the leg 106 and the elastic member 107 closer to the center of gravity than the lower surface of the support member that supports the mechanical unit. Since the amplitude of vibration becomes small, vibration transmission to the refrigerator can be further reduced.

  Moreover, the permanent magnet 151 is used for the rotor 111, the height of the rotor 111 is made low, and the height of the stator 112 is made low by making the stator 112 into a salient pole concentrated winding type. The overall center of gravity can be lowered.

  Further, when the stator 112 is distributed winding, since the winding protrudes upward from the attachment portion of the cylinder block 133 to the stator 112, the dimension of the leg of the cylinder block 133 is larger than the protruding dimension of the winding. However, if the stator 112 is a salient pole concentrated winding type, it is possible to shorten the leg of the cylinder block 133 that is the attachment portion of the cylinder block 133 to the stator 112, and the compression element The center of gravity can also be lowered.

  Further, by extending the extension allowance of the bearing portion 135 of the cylinder block 133 to the rotor recess 111a, the cylinder block 133 can be lowered further and the center of gravity can be lowered.

  As described above, the center of gravity A of the mechanical portion inside the compressor is lowered, and the contact surface 106 between the leg 106 and the elastic member 107 provided in the sealed container 103 outside the compressor is positioned further upward. By doing so, the distance B between the center of gravity A, the contact surface of the leg 106 and the elastic member 107 is further reduced, and vibration transmission from the compressor to the refrigerator can be further reduced.

  This is especially important for refrigerators with a compressor placed at the top, where it is necessary to reduce the overall height of the compressor as much as possible, while at the same time achieving both low vibration and low noise. While various elements for downsizing the compressor are conceivable, in the internal configuration surface, by using the permanent magnet 151 for the rotor 111, while maintaining the holding effect of the rotor 111 by the shaft 130, The bearing portion 135 is further extended into the rotor to reduce the internal height, and on the external configuration surface, the mounting surface of the leg 106 on the elastic member 107 is raised, and the overall height can be increased even when installed in the refrigerator. A low-vibration compact compressor with low center of gravity and high support stability can be realized.

  Further, according to the present embodiment, the contact surface 106a between the leg of the compressor and the elastic member is located above the lower end surface 113b of the support member, whereby the vibration of the compressor generates vibration. After being transmitted downward through the support member from the mechanical part as the source, the direction changes upward and is transmitted to the elastic member 107 via the leg 106. Therefore, since the vibration transmission path becomes complicated, the vibration is further attenuated in the transmission path, and further, the distance from the support member to the contact surface 106a between the leg 106 of the compressor and the elastic member 107 can be increased. In particular, the vibration transmission in a high frequency region is attenuated, and the amplitude of vibration of the contact surface 106a between the leg 106 and the elastic member 107 is reduced. Further, vibration transmission to the refrigerator can be reduced, and unpleasant vibration or It is possible to provide a high-quality refrigerator that does not generate noise due to vibration.

  Further, the leg 106 has a fixing surface 106b that is fixed to the sealed container 103, a bent portion 106c that rises upward, and an elastic member disposing lower surface 106d that locks the elastic member. It is located on the fixed surface 106b of the lower portion of the closed container 103, and the surface on which the elastic member is arranged can be the elastic member arrangement lower surface closer to the center of gravity, by forming the bent portion by simple leg bending, It is very easy to manufacture.

  Further, the fixing surface 106b fixed to the closed container 103 of the leg 106 is below the lower end surface 113b that is the fixing surface of the support member 113a of the lower container 101, and the vibration of the compression element 113 that is the vibration source of the compressor. Is transmitted to the fixing surface of the support member 113a located farthest from the excitation source in the sealed container 103 through the electric element 110 and also through the spring 114 supported by the support member 113a. So the vibration is greatly damped.

  Further, the leg 106 extends from the fixing surface in a substantially horizontal direction, rises vertically upward by the formation of the bent portion 106c, and bends in the substantially horizontal direction again, and then the elastic member disposition lower surface 106d is formed. The vibration transmission path becomes complicated and long up to the contact surface 106a with the member 107, and the vibration transmission is attenuated. Further, the elastic member 107 has a lower elastic member arrangement lower surface 106d closer to the center of gravity A in the vertical direction of the compressor, and the elastic member 107 has a sufficient length. Therefore, vibration transmission to the refrigerator can be sufficiently reduced, and a high-quality refrigerator free from unpleasant vibration and noise caused by vibration can be provided.

  Further, the formation of the bent portion 106c makes it possible to increase the distance from the surface where the leg 106 is fixed to the sealed container 103 to the lower surface where the elastic member 107 is disposed, and transmission of vibration from the fixing surface 106b. Since the distance becomes long, transmission in a particularly high frequency region is attenuated, and vibration transmission to the refrigerator can be reduced. Therefore, manufacture is easy and vibration transmission to the refrigerator can be reduced, and providing a high-quality refrigerator free from unpleasant vibration and noise generation due to vibration can be achieved at low cost.

  Furthermore, by providing the leg 106 with the rib 106e extending over the bent portion 106c and the elastic member arrangement lower surface 106d, the rigidity of the leg 106 is increased, the eigenvalue of the leg 106 itself is increased, and the leg 106 itself vibrates. Therefore, it is possible to further reduce vibration transmission from the fixing surface of the sealed container 103 to the elastic member and the refrigerator main body through the legs. Further, the rib can be formed by a press that is easy to manufacture, and the strength of the leg is increased. Therefore, another problem that the leg is deformed by the transport impact of the refrigerator can be improved.

  Therefore, manufacture is easy and vibration transmission to the refrigerator can be reduced, and providing a high-quality refrigerator free from unpleasant vibration and noise generation due to vibration can be achieved at low cost.

  As described above, the downsizing element in the height direction of the compressor 11 can be broadly distinguished from the viewpoint corresponding to the electric element 110 and the viewpoint corresponding to the compression element 113. Whether to keep it in any one of the elements may be selected based on a balance between a required value for height reduction and other characteristics and quality.

  For example, a method of mainly configuring a height reduction element that is combined with the electric element 110 that does not require relatively high-precision durability and reliability and is not likely to cause significant noise and vibration is a configuration in which the compressor 11 is disposed above. Is advantageous in that it can be downsized while suppressing the effects on noise and vibration.

  On the other hand, when trying to achieve the purpose by downsizing the compression element 113, it is possible to expect a reduction in size by reducing the cost, which is advantageous in terms of cost performance.

  In addition, as described above, the compressor 11 is arranged on the upper part of the box body 1 of the refrigerator so that it is closer to the user's ear, so that it is necessary to consider noise and vibration more than the conventional refrigerator, and the compression Miniaturization by reducing the height of the machine 11 is important in combination with miniaturization elements that do not affect the noise and vibration of the refrigerator, and the structure for supporting the electric element 110 and the compression element 113 and the sealed container 103 are provided. It is also effective to incorporate ingenuity to reduce the height while suppressing noise and vibration in the supporting structure, or to not incorporate a simple height reduction design that adversely affects noise and vibration.

  Next, focusing on the top storage space 29a and the second storage space 30a of the refrigerator, the back of the top storage space 29a is a hard-to-reach place, and the back of the top storage space 29 is closed by the convex portion 30b. Even if it is peeled off, the depth of use becomes shallow, and since there are stored items such as food within the reachable range, it can be prevented from being left behind after the expiration date, and the usability is improved. On the other hand, when the convex portion 30b travels to the second-stage storage space 30a side, the convex portion 30b becomes noticeable when the refrigerating chamber revolving door 5 is opened, and the appearance is deteriorated. There is an inconvenience that food or the like is difficult to put in and take out when storing or taking out the food, but the horizontal surface of the shelf bottom portion 30d of the uppermost storage space 29a and the convex portion 30b that is the indoor side bottom wall surface of the concave portion 27 Are substantially the same horizontal plane, and the compressor 11 can be accommodated in the predetermined recess 27 in a state where the external appearance is almost continuously connected and the protrusion of the protrusion 30b is not felt and the appearance is good. .

  Further, the protruding portion 30b does not feel the protrusion and the appearance is improved, and stored items such as foods lower than the height of the opening of the second stage storage space 30a can be smoothly put in and out, and inconvenience is eliminated.

  Looking more specifically at the dimensions, the distance from the top surface 23 to the shelf bottom 30d of the uppermost storage space 29a is that the heat insulation wall thickness between the top surface 23 and the interior is 25 mm, and the height of the uppermost storage space 29a. Is 140 mm (because it is the uppermost part in the cabinet, the thickness is determined to be 140 mm when taking into consideration that the standard product of a 350 ml can drink with a height of 123 mm and a diameter of 66 mm is tilted and pulled out is 140 mm). Is 10 mm, it is 175 mm. The uppermost housing is provided with the thickness of the installation surface 28b of the compressor 11 of the recess 27 being 20 mm, the clearance between the compressor 11 and the installation surface 28b and the clearance between the inner surface of the top cover 34 being 3 mm each, and the thickness of the top cover 34 being 2 mm. If the shelf bottom 30d of the space 29a and the indoor side bottom wall surface 30c of the recess 27 are substantially the same horizontal plane, the maximum height of the compressor 11 that can be accommodated in the recess 27 is 147 mm.

  On the other hand, when the dimensions of the compressor 11 are seen more specifically, the total thickness of the lower container 101 and the upper container 102 of the sealed container 103 is 7 mm, and the height for obtaining the curvature of the upper container 102 is 14 mm. The upper part of the cylinder block 133 with the compression chamber 134 is 39 mm, the dimension to the stator 112 mounting surface on the side with the bearing portion 135 is 20 mm, the height of the stator 112 is 26 mm, the lower end of the stator 112 to the rotor 111 9 mm, the distance from the lower end of the rotor 111 to the refrigerating machine oil 105 is 9 mm, and the height of the refrigerating machine oil 105 is 20 mm. The total of these is 144 mm. 27 can be accommodated in a height space.

  Thus, since the height dimension of this type of compressor in a refrigerator with a standard capacity is generally 190 mm or more, a large height dimension can be reduced. In particular, by using an inverter motor using a permanent magnet 151 for the rotor 111 that is operated at a plurality of rotation speeds including frequencies higher than those of the commercial power supply, the compression element 113 and the electric element 110 of the compressor 11 can be appropriately dimensioned. The compressor 11 can be accommodated in the predetermined recess 27 while maintaining the rigidity for keeping the noise of the airtight container 103 good, and the convex portion which is the bottom wall surface on the indoor side of the recess 27. By making the horizontal plane of 30b substantially the same horizontal plane, it is possible to provide a refrigerator that is substantially continuous in appearance and does not feel the protrusion of the convex portion 30b and has a good appearance.

  Further, by incorporating the downsizing element in the height direction as the main component of the improvement of the electric element 110, the problem of ensuring the reliability of the noise and the vibration surface associated with the specification change of the compression element 113 is reduced. 11 can be an effective means for reducing the height while solving the problems of noise and vibration for a refrigerator in which noise and vibration are concerned by arranging 11 at the top of the refrigerator.

  In the present embodiment, the ground height of the box body 1, that is, the height of the top surface 23 from the floor surface is set to 1800 mm or less. This height is set based on the maximum height that can be reached by a Japanese woman of standard height reaching up.

  If the height of the top surface 23 from the floor surface is higher than 1800 mm, the height of the compressor 11 can be easily accommodated in the recess 27 without making the height dimension large and compact. Usability becomes even worse, making it difficult to achieve both storage efficiency and usability as a whole refrigerator.

  In the present embodiment, the height of the top surface 23 from the floor surface is suppressed to 1800 mm or less, so that the user-friendliness is first taken into consideration, and then the height of the compressor 11 is made as compact as possible within this height range. This makes it possible to maximize the merit of suppressing the invasion of the effective space inside the warehouse and maximize the storage efficiency.

(Embodiment 5)
FIG. 20 is a schematic cross-sectional view of the refrigerator in the fifth embodiment of the present invention.

  In addition, about the same structure as Embodiment 4, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

  In addition, although configurations and operational effects common to the fourth embodiment will not be described one by one, it is assumed that the same contents are included unless they are unreasonable when applied to the present embodiment.

  In the figure, a ventilation duct 201 communicating with the recess 27 is provided immediately below the top surface 200 of the box body 1, and the top portion 203 of the compressor 11 comes to a position higher than the lower surface 202 of the ventilation duct 201 and lower than the top surface 200. Thus, the compressor 11 is installed on the installation surface 28 b of the recess 27. A condenser 204 is disposed above the ventilation duct 201, and the condenser 204 communicates with the discharge pipe 31. The top surface 200 of the ventilation duct 201 is configured to be substantially the same horizontal plane as the surface of the recess 27 on the top surface cover 34 or integrally. The ventilation duct 201 sucks air from the intake port 205, passes through the concave portion 27 in which the condenser 204 and the compressor 11 are installed, and exhausts the air from the discharge port 206 of the top cover 34.

  In the configuration as described above, the top portion of the compressor 11 is disposed at a position lower than the top surface 200 of the box body 1 and higher than the lower surface 202 of the ventilation duct 201, so the inside of the recess 27 that accommodates the compressor 11. The overhanging margin, that is, the protruding margin of the convex portion 30b is reduced, and the internal space can be utilized more effectively.

  In addition, since the compressor 11 may be designed so that the height of the compressor 11 is within the height range in which the height of the ventilation duct 201 and the height of the recess 27 are combined, for example, a large refrigerator can be used. Even if various elements are incorporated, if a compressor having a relatively large refrigerating capacity must be employed, the degree of freedom in design can be expanded, and the compressor 11 can be used even in a large refrigerator. It becomes easy to provide a refrigerator with high storability that is stored behind the top.

  On the other hand, the ventilation duct 201 necessary for cooling the compressor 11 is disposed on the top surface 200 that is difficult to reach in the refrigerator, so that the vicinity of the top surface 200 can be effectively used for purposes other than storage. Further, since the top 203 of the compressor 11 is disposed at a position lower than the top surface 200 of the box body 1 and higher than the lower surface 202 of the ventilation duct 201, the top of the compressor 11 is projected in the ventilation direction of the ventilation duct 201. By being arranged in the plane, the top portion 203 having the highest temperature in the compressor 11 is efficiently cooled, and the characteristics and reliability of the compressor 11 are also improved. Furthermore, by configuring the condenser 204 inside the ventilation duct 201, the heat dissipation effect of the condenser 204 is enhanced, and the efficiency of the system can be improved.

  Next, focusing on the uppermost storage space 29a and the second storage space 30a of the refrigerator, the back of the uppermost storage space 29a is a place that is difficult to reach, and the back side of the uppermost storage space 29a is closed by the convex portion 30b. Even if it is peeled off, the depth of use becomes shallower, and stored items such as foods are within the reach of the hand. Therefore, it is possible to prevent the product from being left behind after the expiration date, and the usability is improved. On the other hand, when the convex portion 30b travels to the second-stage storage space 30a side, the convex portion 30b becomes noticeable when the refrigerating compartment revolving door 5 is opened, the appearance looks worse, and food or the like is behind the second-stage storage space 30a. There is an inconvenience that food or the like is difficult to put in and take out when storing or taking out, but the shelf bottom portion 30d of the uppermost storage space 29a and the inner bottom wall surface 30c of the recess 27 are substantially omitted. By adopting the same horizontal plane, the compressor can be accommodated in the predetermined recess 27 in a state where the external appearance is almost continuously connected and the protrusion of the protrusion 30 b is not felt and the appearance is good.

  The substantially identical horizontal plane refers to the case where the indoor side bottom wall surface 30c of the recess 27 and the shelf bottom portion 30d of the uppermost storage space 29a are substantially the same horizontal plane, or the indoor side bottom wall surface 30c of the recess 27 and the uppermost stage In some cases, the upper side of the shelf, which is the lower end of the storage space 29a, may be substantially the same horizontal plane, and the shelf that forms the uppermost storage space 29a is positioned in the vicinity of the indoor side bottom wall surface 30c of the recess 27. The compressor can also be accommodated in the predetermined recess 27 in a state in which the protrusion 30b does not feel the bulge and the appearance is good.

  In addition, stored items such as food that are lower than the height of the frontage of the second-stage storage space 30a can be smoothly put in and out, and there is no inconvenience.

  In addition, since the uppermost storage space 29a is located at a high position and is difficult to store, the minimum height at which a 350 ml canned beverage standard product (123 mm in height) can be stored in order to reduce the height of the storage portion as much as possible. If this is the case, setting the height of the storage portion of the uppermost storage space 29a to 125 mm with a gap of 2 mm in the upper part can be used most efficiently.

  More specifically, in the refrigerator shown in the figure, the distance from the shelf bottom 30d of the uppermost storage space 29a to the top surface 200 including the ventilation duct 201 and the top surface of the top cover 34 is determined by the ventilation duct 201. The thickness of the top surface 200 to be formed is 2 mm, the inner height of the ventilation duct 201 is 18 mm, the heat insulation wall thickness between the lower surface 202 of the ventilation duct 201 and the interior is 25 mm, and the height of the uppermost storage space 29a is 350 ml. If the standard height of 125 mm where a canned beverage standard product enters is 125 mm and the shelf board thickness is designed to be 10 mm, then 180 mm. The uppermost housing is provided with the thickness of the installation surface 28b of the compressor 11 of the recess 27 being 20 mm, the clearance between the compressor 11 and the installation surface 28b and the clearance between the inner surface of the top cover 34 being 3 mm each, and the thickness of the top cover 34 being 2 mm. If the shelf bottom portion 30d of the space 29a and the indoor side bottom wall surface 30c of the concave portion 27 are substantially the same horizontal plane, the maximum height of the compressor 11 that can be accommodated within the combined height of the concave portion 27 and the ventilation duct 201 is 152 mm. Yes, the compressor 11 having a height dimension of 144 mm shown in the first embodiment can be sufficiently designed for housing and can easily meet the demand for increasing the size of the compressor in response to the increase in size of the refrigerator. It becomes.

  In addition, even when the compressor 11 having a height dimension of 144 mm shown in the first embodiment is used and the height of the elastic member is 20 mm or more, by raising the legs of the compressor upward, The height up to the top of the container can be 155 mm or less, which makes it possible to install a compressor that can be mounted with low vibration and low noise even in a refrigerator of a type that is restricted in the height direction of the machine room. Furthermore, since the height of the elastic member can be sufficiently increased, a compressor with lower noise can be realized.

  That is, the balance between the storage space cut into the compressor 11 and the uppermost storage space is harmonized in appearance, and is usually unusable. The rear space, which is particularly inconvenient, is applied to the compressor housing recess 27, and the can beverages that are often housed in a refrigerator are arranged vertically in the front space that is relatively easy to use. Since it can be stored, the number of storage in the entire refrigerator compartment increases, and the uppermost storage space 29a can be effectively utilized.

  As described above, the ventilation duct 201 communicating with the recess 27 is provided to be the top surface 200 of the box body 1, and the top portion 203 of the compressor 11 is lower than the top surface 200 of the box body 1, and the bottom surface 202 of the ventilation duct 201. Since the ventilation duct 201 necessary for cooling the compressor 11 and the like is arranged near the top surface 200 which is difficult to reach and is not easy to use, the vicinity of the top surface 200 is stored. It can be used effectively for other purposes, and the storage in the cabinet is also improved. Moreover, since the top 203 of the compressor 11 is disposed at a position lower than the top surface 200 of the box body 1 and higher than the lower surface 202 of the ventilation duct 201, the top 203 having the highest temperature in the compressor 11 is efficiently cooled. Also, the characteristics and reliability of the compressor 11 are improved.

(Embodiment 6)
FIG. 21 shows a schematic diagram of the refrigerator in the sixth embodiment of the present invention, and FIG. 22 is a solubility curve diagram of the refrigerant and the refrigerating machine oil in the same embodiment.

  The refrigerator main body 601 is provided with a refrigerating room 602 that is a relatively high temperature compartment in the upper part and a freezing room 604 that is a relatively low temperature compartment in the lower part, and has a so-called bottom freezer configuration. Yes. The refrigerator compartment 602 and the freezer compartment 604 are configured to be insulated from the surroundings with a heat insulating material such as urethane. Moreover, taking in and out of stored items such as food is performed through a heat insulating door (not shown).

  The refrigerator compartment 602 is usually set at 1 to 5 ° C. for refrigerated storage, but may be set at a slightly lower temperature, for example, −3 to 0 ° C. to improve the freshness, and may be used depending on the stored items. In some cases, a person can freely switch the temperature setting as described above. In addition, in order to preserve wine, root vegetables, etc., the temperature may be set slightly higher, for example, around 10 ° C.

  The freezer compartment 4 is usually set at −22 to −18 ° C. for frozen storage, but may be set at a lower temperature, for example −30 to −25 ° C., for improving freshness.

  The machine room 11 is configured on the upper surface of the refrigerator body 601, and the bottom surface of the machine room 611 is provided at a position lower than the first top surface part 613 and the first top surface part 613 on the back surface 614 side of the refrigerator outer box. The second top surface portion 615 is formed in a step shape. The condenser 616 is disposed in the upper space portion of the first top surface portion 613, and the compressor 612 is disposed in the upper space portion of the second top surface portion 615, and is made of a resin that covers the condenser 616 and the compressor 612. A machine room cover 617 serving as a cover is fixed to the refrigerator main body 1 with screws or the like.

  Here, since the evaporator 609 is disposed behind the freezer compartment 604, the height relationship between the compressor 612 and the evaporator 609 is such that the compressor 612 is disposed on a part of the top surface of the refrigerator body 601. The evaporator 609 is arranged in a part near the lower part, and the refrigerant return path in the refrigeration cycle from the evaporator 609 to the compressor 612 has a relation of having a considerable rising distance in the height direction. .

  The refrigeration cycle 618 is formed of a series of refrigerant flow paths that are sequentially provided with a compressor 612, a condenser 616, a capillary 619 that is a decompressor, and an evaporator 609.

  The compressor 612 is a reciprocating compressor that compresses refrigerant by reciprocating a piston in a cylinder.

  Further, the compartment of the machine room 611 includes a first top surface part 613, a second top surface part 615, and a machine room cover 617.

  In the case of a refrigeration cycle 618 using a three-way valve or a switching valve, the functional component may be disposed in the machine room 611 in the refrigerator main body 601.

  Further, in the present embodiment, the decompressor constituting the refrigeration cycle 18 is the capillary 619, but there may be an electronic expansion valve that can freely control the flow rate of the refrigerant driven by the pulse motor.

  The operation and action of the refrigerator configured as described above will be described below.

  The high-temperature and high-pressure refrigerant discharged by the operation of the compressor 612 exchanges heat with the air above the refrigerator main body 601 in the condenser 616 to dissipate heat and condensate into the capillary 619. Thereafter, the pressure is reduced by the capillary 619 while exchanging heat with the suction line 620, and the evaporator 9 is reached.

  Due to the action of a cooling fan (not shown), the cool air having a relatively low temperature due to the evaporation action of the refrigerant in the evaporator 609 flows into the refrigerating room 602 and the freezing room 604, and the respective rooms are cooled. In the evaporator 609, the refrigerant that has exchanged heat with the air in the warehouse then passes through the suction line 620 and is sucked into the compressor 612 together with the refrigerator oil.

  Thus, when the refrigeration cycle 618 is configured such that the compressor 612 is disposed above the evaporator 609, the compressor 612 is disposed on a part of the top surface of the refrigerator main body 1 as in the present embodiment. When the evaporator is arranged near the lower part of the refrigerator main body 601 and the rising distance of the return path of the refrigerant from the evaporator 609 to the compressor 612 becomes large, the refrigerant 612 and the refrigerant together with the refrigerant in the refrigeration cycle 618 An important point regarding the reliability of the compressor 612 is how to return the refrigeration oil discharged to the compressor 612 through the suction line 620 to the accumulator (not shown) in the evaporator 609.

  Further, regarding the return characteristics of the refrigeration oil in the start-up pipe, it is widely known that the flow rate of the refrigerant in the pipe depends more greatly, although the influence of the viscosity of the refrigeration oil can be considered.

  However, if the refrigerant flow rate is increased by increasing the cylinder capacity of the compressor 612 or increasing the rotational speed of the compressor 612 in order to secure the refrigerant flow rate, the evaporator flow rate will be increased. This causes a decrease in the evaporation temperature of 609, increases the compression ratio of the compressor 612, and increases the amount of power consumption. Therefore, it has been difficult to solve by these means.

  Therefore, in the present embodiment, for example, isobutane, which is a hydrocarbon refrigerant, is used as the refrigerant of the refrigeration cycle 618.

  (Table 1) shows physical properties in a saturated liquid of −30 ° C. of isobutane and a conventional alternative chlorofluorocarbon refrigerant such as R134a.

  As shown in Table 1, the refrigeration capacity per unit volume of isobutane is 520.8 kJ, whereas the refrigeration capacity per unit volume of R134a, which is a conventional alternative chlorofluorocarbon refrigerant, is 971.6 kJ. Compared with R134a, the refrigerating capacity per unit volume is about ½. Therefore, in order to make the refrigeration capacity of the compressor 612 equivalent to that of the conventional R134a, the cylinder volume of the compressor 12 is increased to about twice, and the displacement of the piston per unit time of the compressor 612 is also about the same. It increases to about 2 times. That is, since the volume flow rate of the refrigerant per unit time increases, the flow velocity in the pipe during the operation of the compressor 612 increases to about twice.

  Moreover, the refrigerating capacity per unit volume of CO2, which is a natural refrigerant, is 11258.5 kJ, and isobutane has a refrigerating capacity per unit volume of about 1/20 compared with CO2. Therefore, in order to make the refrigerating capacity of the compressor 12 equal to CO2, the cylinder volume of the compressor 612 is increased to about 20 times, and the piston displacement per unit time of the compressor 612 is also about 20 times as well. Increases to a degree. That is, since the volume flow rate of the refrigerant per unit time increases, the flow velocity in the pipe during the operation of the compressor 12 increases to about 20 times.

  As a result, even when the compressor 612 is disposed above the evaporator 609, the refrigerating machine oil staying in the evaporator 609 can be quickly returned to the compressor 612, and the refrigerating machine oil in the compressor 612 is insufficient. Therefore, the risk of damage to the compressor 612 can be reduced.

  In addition, the refrigerant staying in the evaporator 609 is returned to the compressor 612 together with the refrigerant due to the thermosiphon effect of the refrigerant when the evaporator 609 is defrosted by the action of a defrosting heater (not shown). It is. However, especially when the compressor 612 is disposed above the evaporator 609 and the suction line 620 as a start-up pipe is long, if the solubility of the refrigerant in the refrigerating machine oil is small, the refrigerant is transferred to the compressor 612 together with the refrigerant. There was also a problem that the return amount of the refrigerating machine oil to be transported decreased.

  Therefore, mineral oil having good compatibility with isobutane is used as the refrigerating machine oil for the refrigerating cycle 618.

  FIG. 22 is a comparison of solubility curves obtained when a conventional combination of, for example, R134a and ester oil is used, and when the isobutane and mineral oil of the present embodiment are combined. The horizontal axis represents the temperature of the refrigerant in the evaporator 609 (evaporation temperature), and the vertical axis represents the solubility (mass%) of the refrigerant dissolved in the refrigeration oil. According to this, the solubility increases in any case as the evaporation temperature in the evaporator 609 increases, but the difference increases as the evaporation temperature increases. Usually, defrosting of the evaporator 609 is performed until the evaporator 609 reaches about 10 ° C. in anticipation of safety after the frost adhering to the evaporator 609 is melted. Therefore, when compared at a point where the temperature of the evaporator 609 is 10 ° C., the solubility when isobutane and mineral oil are combined is increased to about 50% as compared with the conventional case where R134a and ester oil are combined.

  As a result, even when the compressor 612 is disposed above the evaporator 609 and the entire length of the suction line 620 that is a start-up pipe becomes long, the thermosiphon effect of the refrigerant is used together with the refrigerant during the defrosting. The amount of refrigerating machine oil returning from the compressor to the compressor 612 can be increased.

  When the compressor is an internal high-pressure type, since the refrigeration oil sprayed in the internal space of the sealed container is discharged out of the compressor together with the discharge refrigerant, the compressor 612 of the present embodiment is an internal low-pressure type, As a result, the amount of refrigerating machine oil discharged from the compressor 612 into the refrigerating cycle 618 can be suppressed, so that the absolute amount of refrigerating machine oil remaining in the refrigerant piping related to the returnability of the refrigerating machine oil can be reduced. It is possible to further reduce the risk of damage to the compressor 612 due to the shortage of the refrigerating machine oil, and to further suppress the efficiency reduction of the heat exchanger such as the evaporator 609 and the condenser 616 due to the staying refrigerating machine oil in the refrigerant pipe. it can.

  Moreover, even when the heat insulation performance of the refrigerator main body 601 is improved by, for example, reducing the thermal conductivity of urethane constituting the refrigerator main body 601, application of a vacuum heat insulating material, or the like, and there is a need to reduce the capacity of the compressor 612, As described above, the combination of isobutane, mineral oil, and the internal low-pressure compressor 612 makes it easy to secure the necessary refrigerating machine oil in the compressor 612.

  In this embodiment, since the reciprocating compressor that compresses the refrigerant by reciprocating the piston in the cylinder is used as the compressor, the piston and the cylinder are separated from each other in comparison with the rotary compressor. Can be managed with relatively high accuracy. Therefore, sufficient sealing performance can be secured without using a large amount of refrigerating machine oil to seal between the piston and the cylinder, and the amount of refrigerating machine oil discharged together with the refrigerant discharged through the cylinder is also reduced. Therefore, the amount of refrigerating machine oil discharged from the compressor can be reduced, and the risk of damage to the compressor 12 due to the shortage of refrigerating machine oil in the compressor 12 can be further reduced.

  Even if the compressor 612 is disposed above the evaporator 609 due to the above-described effect of the combination of isobutane, mineral oil, and the internal low-pressure compressor, even if the distance between the compressor 612 and the evaporator 609 is increased, for example, As in the present embodiment, the compressor 612 is arranged on a part of the top surface of the refrigerator main body 601, the evaporator is arranged near the lower part of the refrigerator main body 601, and the refrigerant returns from the evaporator 609 to the compressor 612. Even when the rising distance of the path becomes large, the reliability of the refrigerator can be sufficiently ensured.

  Accordingly, when a plurality of storage rooms having different temperature bodies are provided in the refrigerator main body 601, the evaporator 609 can be provided in a storage room other than the uppermost storage room, and the compressor 612 becomes hot during operation. By moving the evaporator 609 away from the compressor 612, the condenser 616, etc., the cooling loss of the evaporator 609 due to the effect of exhaust heat from the high temperature part can be reduced, and the refrigeration capacity of the evaporator 609 can be utilized to the maximum, so that power consumption The amount can be reduced.

(Embodiment 7)
FIG. 23 shows a schematic cross-sectional view of the refrigerator in the seventh embodiment of the present invention, FIG. 24 shows a schematic rear view of the refrigerator in the same embodiment, and FIG. 25 shows the refrigerator in the same embodiment. FIG. 26 is a schematic perspective view of a main part of a suction pipe of the refrigerator in the embodiment, and FIG. 27 is a schematic sectional view of a compressor mounted on the refrigerator in the embodiment. FIG. 28 shows a schematic sectional view of the refrigerator transported state in the embodiment, and FIG. 29 shows a schematic sectional view of the compressor in the refrigerator transported state in the embodiment.

  In the figure, a heat insulating box 701 is formed by injecting a heat insulating body 715 for foam filling into a space formed by an inner box 713 obtained by vacuum molding a resin body such as ABS and an outer box 714 using a metal material such as a pre-coated steel plate. Insulated walls. As the heat insulator 715, for example, a hard urethane foam, a phenol foam, a styrene foam, or the like is used. Use of hydrocarbon-based cyclopentane as the foaming material is better from the viewpoint of preventing global warming.

  The heat insulation box 701 is divided into a plurality of heat insulation sections, and has a configuration in which the upper part is a revolving door type and the lower part is a drawer type. From the top, there are a refrigerator room 702, a drawer type switching room 716 and an ice making room 717 provided side by side, a drawer type vegetable room 703 and a drawer type freezer room 704. Each heat insulation section is provided with a heat insulation door via a gasket 718. From the top are a refrigerating room rotary door 705, a switching room drawer door 719, an ice making room drawer door 720, a vegetable room drawer door 706, and a freezer compartment drawer door 707.

  The refrigerator compartment rotary door 705 is provided with a door pocket 721 as a storage space, and a plurality of storage shelves 722 are provided in the storage. A storage case 723 is provided at the bottom of the refrigerator compartment 702.

  In addition, the outer box 714 of the heat insulating box 701 is a machine that forms a shell 724 obtained by U-bending a steel plate whose top surface is cut off, a bottom panel 725, a back panel 726, and a recess 727 in which the back of the top surface is recessed. The chamber panel 728 is assembled with a sealing property secured. The machine room panel 728 is formed by drawing a steel plate, and the corner portion has an R shape for improving workability. This R shape secures a flow path of the branching or joining portion of the heat insulating body 715 to be foam-filled to improve fluidity, and can prevent generation of voids due to insufficient filling.

  The machine room panel 728 has the deepest arrangement part of the compressor 711, and the shape of the throttle is shallower toward the left and right ends. Is improved.

  Furthermore, since the machine room panel 728 is drawn, it is advantageous in terms of man-hours because it requires less sealing parts for foam filling, and if a similar shape is formed by sheet metal processing, the cost of the drawing die is reduced. In addition, the finish can be reduced and the dimensional accuracy can be improved.

  In addition, the machine room panel 728 is provided with a plurality of air vent holes (not shown) on each surface, and can prevent the generation and deformation of voids due to residual air without impairing the appearance and internal appearance.

  Further, the bottom panel 725 and the back panel 726 are provided with handles made of depressions that can be hooked with fingertips. The bottom handle 729 is provided at a predetermined interval at two positions so that a fingertip can be applied from the front at a position from the front to the center of the bottom. The back handle 730 is provided at a predetermined interval at two positions so that the fingertip can be put upward at a position as high as possible at the top of the back panel 726.

  In addition, the inner box 713 is slightly smaller than the outer box 714, and the rear back portion is recessed inward, and the space in which the heat insulating body 715 is foam-filled by being incorporated in the outer box 714 is a heat insulating box. 701 is formed. Therefore, the right and left parts of the machine room panel 728 are also filled with the heat insulating body 715 to form heat insulating walls, and the strength is ensured. Further, the strength of the bottom surface handle 729 and the back surface handle 730 is ensured by the heat insulating body 715 filled with foam.

  Further, the refrigeration cycle includes a compressor 711 elastically supported in the recess 27, a machine room fan 731 provided in the vicinity of the compressor 711, a top surface of the shell 724, a recess 727, a bottom panel 725, A condenser (not shown) provided on the side surface of the shell 724, a capillary 732 as a decompressor, a dryer (not shown) for removing moisture, a cooling fan 708 on the back of the vegetable compartment 703 and the freezing compartment 704 Are arranged in the vicinity of an evaporator 709 and a suction pipe 733 connected in a ring shape.

  The recess 727 is provided with a top cover 734 fixed with screws or the like, and houses a compressor 711, a condenser (not shown), a machine room fan, a dryer, a pipe, and the like provided in the recess 727. It is.

  The capillary 732 and the suction pipe 733 are copper pipes having substantially the same length, and are soldered so as to be able to exchange heat, leaving the end portions. The capillary 732 uses a thin copper tube having a large internal flow resistance for pressure reduction, and the inside diameter is about 0.6 mm to 1.0 mm and is adjusted with the length to design the amount of pressure reduction. The suction pipe 733 uses a large-diameter copper pipe to reduce pressure loss, and the inner diameter is designed to be about 6.35 mm to 7.94 mm. Further, in order to ensure the length of the heat exchanging portion 735, it is meandered to be compact and arranged in the middle of the inner box 713 and the back panel 726 so that the meandering portion comes to the back of the refrigerator compartment 702. Embedded in the body 715. One end of the capillary 732 and the suction pipe 733 protrudes from the rear position of the vegetable compartment 703 of the inner box 713 and is connected to the evaporator 709, and the other end is provided with a notch ( It protrudes upward from an unshown) and is connected to a dryer (not shown), a condenser and a compressor 711, respectively.

  In addition, since the piping is taken in and out from the rear of the vegetable room 703 having a relatively high temperature, the effect of increasing the amount of heat that enters due to the piping is small and effective in reducing energy consumption.

  The suction pipe 733 is provided with an oil outflow prevention trap 736 in the vicinity of the connection portion with the compressor 711, and is accommodated in the recess 727. With the aim of improving assembly workability and service workability, the pipe connection part of the compressor 11 faces the back side in order to reduce the density of the pipes and to make the pipe connection part visible from the rear. Are arranged separately on the left and right sides of the compressor.

  The suction pipe 733 is linearly provided with a slight upward gradient from the lower side on the back side of the compressor 711, and is then substantially vertically higher than the vertical center line of the compressor 711 and higher than the compressor 711. A rising part is provided to a lower position. In order to minimize the recess 727 and minimize the protrusion into the refrigerator compartment, it is necessary to reduce the size of the compressor 711 and the space between the peripheral wall of the compressor as small as possible. By setting the pipe height below the height of 711, the wall surface contact of the pipe can be prevented.

  Further, the suction pipe 733 is provided with an oil outflow prevention trap 736 composed of a pipe U-bending portion 737 provided in the front direction of the heat insulating box 701 after being raised in the vertical direction. It is located in the front side of a heat insulation box rather than the plane direction centerline. Since the compressor 711 has a shape with a curvature toward the top surface, if the pipe bending portion 737 is formed above the compressor 711, there is a space, and the pipe storage space is not reduced and the size is reduced. Is possible. Further, by providing the pipe U-bending portion 737, the elasticity of the pipe can be provided, vibration propagation from the compressor 711 can be absorbed, stress concentration at the pipe fixing portion can be prevented, and the risk of pipe breakage can be reduced.

  The suction pipe 733 is bent in a substantially vertical direction after being bent in the U direction, and is embedded in the heat insulator 715 from the rear end portion of the machine room panel 728.

  The internal structure of the compressor 711 will be described.

  In FIG. 25, the periphery of the shell joint portion 740a, which is an overlapped portion of a bowl-shaped lower shell 738 formed by deep drawing a thick steel plate of 2 to 4 mm and an inverted bowl-shaped upper shell 739, is combined. A rotary drive unit 742 and a compression unit 743 that are elastically supported by an elastic body 741 inside a compressor-shell 740 having a hermetically sealed structure connected by welding, and a suction pipe 733 having an open end inside the compressor shell 740, and a discharge A pipe 744 is connected to other devices constituting the refrigeration cycle, and a predetermined amount of oil 745 and a refrigerant (not shown) are enclosed. Further, a support portion 746 for elastically supporting the heat insulating box 701 is attached to the lower portion of the lower shell 738. The support portion 746 is provided with a relief for securing the thickness of the elastic support member by one step.

  The rotation drive unit 742 includes a motor 747 and a bearing unit 748, and the motor 747 has a stator 749 having a hollow cylindrical electromagnetic coil that generates a rotational force between a permanent magnet and a voltage applied thereto, and a hollow portion inside the stator 749. And a rotor 750 having permanent magnets opposed to each other with a minute gap, and the bearing portion 748 is provided with an eccentric shaft 751 at the end, is hollow at both ends, and has a spiral groove (not shown) around it. The shaft 752 is provided with a jet hole that communicates with the shaft 752, and a bearing 753 that rotatably holds the shaft 752.

  The compression unit 743 is attached to a cylinder 755 provided with a cylinder head 754 having a valve mechanism (not shown) at the tip, a piston 756, a piston 756, and an eccentric shaft 751 so as to be freely swingable, and a rotation operation is linearly reciprocated. It is comprised with the rod 757 converted into operation | movement. A discharge pipe 744 is connected to the cylinder head 754 via a valve mechanism so that the compressed refrigerant is directly discharged to the outside of the compressor shell 740, and the suction portion is connected to the compressor shell 740 via the valve mechanism. It is open inside. In particular, for the purpose of silencing, a silencing muffler (not shown) is arranged between the suction path of the cylinder head 754 and the machine room shell 740 in the suction path.

  Note that the suction pipe 733 is arranged so that the opening end thereof is flush with the inner wall surface of the compressor shell 740, thereby reducing the size of the compressor 711.

  About the refrigerator comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  First, the temperature setting and cooling method of each heat insulation section will be described. The refrigerator compartment 702 is normally set at 1 to 5 ° C. with the temperature at which it is not frozen for refrigerated storage as the lower limit. Further, the storage case 723 is set at a relatively low temperature, for example, −3 to 1 ° C., for improving the freshness of meat fish and the like.

  The switching chamber 716 can change the temperature setting according to the user setting, and can be set to a predetermined temperature setting from the freezer compartment temperature zone to the refrigeration and vegetable compartment temperature zones. In addition, the ice making chamber 717 is an independent ice storage chamber, and includes an automatic ice making device (not shown) to automatically produce and store ice. Although it is a freezing temperature zone for storing ice, it can also be set at a freezing temperature of −18 ° C. to −10 ° C., which is relatively higher than the freezing temperature zone for the purpose of storing ice.

  The vegetable room 703 is often set to a temperature setting of 2 ° C. to 7 ° C., which is equal to or slightly higher than that of the refrigerator compartment 702. It is possible to maintain the freshness of leafy vegetables for a long period of time as the temperature is lowered so as not to freeze.

  The freezer compartment 704 is normally set at −22 to −18 ° C. for frozen storage, but may be set at a low temperature of −30 or −25 ° C., for example, to improve the frozen storage state.

  Each chamber is divided by a heat insulating wall in order to efficiently maintain different temperature settings. However, as a method of improving the heat insulating performance at a low cost, it is possible to integrally foam and fill with the heat insulating body 15. Compared to the use of a heat insulating member such as polystyrene foam, the heat insulating performance can be increased by about twice, and the storage volume can be increased by thinning the partition.

  Next, the operation of the refrigeration cycle will be described. The cooling operation is started and stopped by a signal from a temperature sensor (not shown) and a control board according to the set temperature in the cabinet. A voltage is applied through a wire from a terminal (not shown) to the motor 747 of the rotation drive unit 742 in the compressor 11 in accordance with the instruction of the cooling operation.

  When the motor 747 is operated, the electromagnetic coil of the stator 749 is excited to generate a rotational force with the rotor 750 having a permanent magnet. The rotation of the rotor 750 causes the shaft 752 fixed to the rotor 750 in the bearing portion 748 to rotate synchronously, and the eccentric shaft 751 also rotates eccentrically. The piston 756 reciprocates in the cylinder 755 through a rod 757 that is swingably provided by the rotation of the eccentric shaft 751.

  Thereby, the compression operation of the refrigerant gas is performed in the compression unit 743. That is, when the piston 756 moves to the position farthest from the cylinder 755, the pressure in the cylinder 755 decreases, and the valve mechanism (not shown) of the suction portion provided in the cylinder head 754 is opened, and the compressor The refrigerant gas in the shell 740 is sucked into the cylinder 755 via a muffler muffler (not shown). Next, when the piston 756 moves to the position closest to the cylinder 755, the sucked refrigerant gas is compressed and becomes a high-temperature and high-pressure refrigerant gas and is discharged from the discharge portion of the cylinder head 754 via the valve mechanism. The discharged refrigerant gas is sent out of the compressor shell 740 through a discharge pipe 744 directly connected to the cylinder head 754.

  Thus, the compressor shell 740 has an internal low-pressure type structure in which low-pressure refrigerant gas exists, and the refrigerant gas returning from the suction pipe is discharged into the compressor shell 740.

  The sliding portion 758 present in the bearing portion 748 and the compression portion 743 of the compressor 711 is ensured to be lubricated by the oil 745. Furthermore, a compatible combination of oil 745 and refrigerant gas is selected, and a combination of R134a and ester oil having a low ozone depletion coefficient, and particularly a hydrocarbon refrigerant HC600a which has a low global warming coefficient and is good for environmental protection. And mineral oil.

  The oil 745 is enclosed in the compressor shell 740, and the amount of the oil 745 is determined so as to be stored in the lower part to ensure a predetermined oil surface height. The oil 745 is supplied to the sliding portion 758 by being transmitted through the hollow interior of the shaft 752 by centrifugal force generated by the rotation of the shaft 752. The lower end of the shaft 752 is completely attached to the oil 745, and the oil 745 that goes back from the inside of the shaft 52 from here is sprayed from an ejection hole (not shown) provided at a position facing each part of the sliding portion 758. ing. Further, the oil 745 can be sufficiently supplied to the sliding portion 758 by the spiral groove around the shaft 752.

  The high-temperature and high-pressure refrigerant discharged by the operation of the compressor 711 as described above dissipates heat in a condenser (not shown) to be condensed and liquefied, and is depressurized by the capillary 732 to become a low-temperature and low-pressure liquid refrigerant. To.

  By the operation of the cooling fan 708, heat is exchanged with the air in the cabinet, and the refrigerant in the evaporator 709 is evaporated, and the low-temperature cold air after the heat exchange is distributed by a damper (not shown) or the like. Cooling takes place.

  The refrigerant exiting the evaporator 709 is sucked into the compressor 711 through the suction pipe 733. At this time, since the suction pipe 733 is soldered so as to exchange heat with the capillary 732 and embedded in the heat insulator 715, heat is transferred from the low-temperature suction pipe 733 to the high-temperature capillary 732 without escape of heat to the surroundings. Since the capillary 732 is cooled in the process of depressurizing the refrigerant, the specific enthalpy is reduced and the refrigeration effect is increased. The suction pipe 733 rises in refrigerant temperature, and can be made substantially equal to or higher than the ambient temperature at the outlet. Since the refrigerant temperature in the suction pipe 733 rises, the heat loss in the process of being sucked into the compressor 711 is small, and the efficiency is improved. The refrigeration cycle that generates the refrigeration temperature has a very low effect of reducing heat loss because the refrigerant temperature in the evaporator 709 is very low, such as −20 ° C. or less.

  In addition, since the capillary 732 is relatively high in temperature, if it is placed in a low temperature region, heat is dissipated in addition to heat exchange with the suction pipe 733, resulting in heat loss in the refrigeration cycle and a heat load on the inside of the cabinet, reducing energy savings. However, since the capillary 732 and the suction pipe 733 are disposed on the back of the refrigerator compartment 702 having a high internal temperature, it is possible to ensure energy saving without greatly increasing heat loss and heat load on the internal storage. In particular, the heat exchanging portion 735 has a sufficient length and is meandered in the back of the refrigerator compartment 2 so as to be stored compactly, so that energy saving and sufficient temperature rise of the suction pipe 733 can be obtained. Since the ascending gradient is provided and the trap is not provided, the liquid refrigerant and the refrigeration oil are not retained, and the performance influence such as pressure loss is not caused.

  When transporting or moving the refrigerator performing the above operation, it is transported by a plurality of persons, such as four people, using the bottom handle 729 and the back handle 730 provided on the bottom panel 725 and the back panel 726 as shown in FIG. It is like that.

  The weight of refrigerators has increased significantly with the increase in the amount of additional parts accompanying the increase in internal volume and high functionality, and the increase in the use of high-density vacuum insulation materials for energy savings. However, the height is nearly 1800mm, and the width and depth are about 600mm to 750mm, so the device for transportation has become very important.

  When the refrigerator is delivered to the customer, it is necessary to have a sideways transporting form. For this reason, handles are provided on the bottom and upper back. Also, refrigerators are often laid down and transported immediately before the power is turned on, such as during moving and redesigning as well as during delivery.

  With these handle configurations, the refrigerator can be transported with the door surface facing upward, the door is opened unexpectedly during transportation, making it unsafe for the transporter, and problems such as falling parts and stored items in the warehouse. Can be prevented.

  At this time, as shown in FIG. 27, the inside of the compressor 711 provided in the concave portion 727 on the top surface is such that the open end of the suction pipe 733 opened in the compressor shell 740 is submerged in the oil 745. Thus, a backflow outflow is possible from the suction pipe 733, but the oil outflow prevention trap 736 composed of the pipe U-bending portion 737 rises upward with respect to the staying surface of the oil 745 during transportation. Therefore, the oil 745 does not flow out into the suction pipe 733 and the evaporator 709. At the time of re-installation after transportation, the oil 745 in the oil spill prevention trap 736 returns to the compressor shell 740 by gravity and does not leave the suction pipe 733 closed with the oil 745.

  As a result, a predetermined amount of oil 745 in the compressor shell 740 is secured to prevent insufficient lubrication of the sliding portion 758, and in particular, insufficient lubrication of the sliding portion 758 when the power is turned on for the initial start of the compressor 711. Therefore, a highly reliable refrigerator that can further reduce the risk of damage to the compressor 711 can be provided.

  In addition, in order to minimize pulling in the interior of the recess 727, the condenser may be thin and disposed on the top surface, or as a box-shaped configuration, a compressor 711 and a machine room fan 731 are provided in the recess 727. May be arranged in parallel to secure the internal volume in the vertical direction, and if the condenser increases the external surface area such as the fin tube type, wire tube type, spiral fin tube type, etc. It is effective in reducing the size of the condenser and saving energy by increasing its capacity.

  The condenser is not limited to the forced air cooling type, but may be a natural air cooling type composed of copper piping adhered to the inside of the outer box 723 with good heat transfer, or arranged in a partition between the heat insulating doors in each room. You may combine and combine the copper piping for performing drip-proof prevention.

  In addition, when HC R600a is used as the refrigerant, the specific volume of the refrigerant gas is larger and the volume flow rate is increased, so the flow rate of the heat exchanging portion is also increased, heat transfer is promoted, the temperature of the suction pipe 733 is increased, and the capillary 732 The effect is improved with respect to the increase in the refrigeration effect due to cooling, and the compatibility with the refrigerant is large, and the gas flow rate is also large, so that the circulation of the oil 745 is good, which is advantageous in terms of ensuring reliability.

  In addition, by using flow control means such as an electric three-way valve and an electric expansion valve, a plurality of evaporators are used properly according to the compartment configuration and temperature setting configuration, a plurality of capillaries are switched, and the pressure reduction amount is controlled. In addition, further energy saving can be achieved by cutting the gas while the compressor 711 is stopped. In particular, by providing the flow path control means in the recess 727 on the top surface of the heat insulating box 701, it is possible to reduce the heat load on the inside of the cabinet, and to further save energy.

  In addition, the rear handle 730 for carrying the refrigerator is provided below the recessed portion 727 where it is easy to ensure the strength. However, if the control board is provided in the center at the same position and the rear handles 730 are provided on both sides, the rear handle 730 can be arranged efficiently. There is an effect of expanding the internal volume. Further, if the rear handle 730 is provided by being distributed to the left and right above the top cover 734, the installation space of the compressor 711 can be escaped to form a handle shape, so that the space efficiency is good, and the corner portion of the heat insulating box 701 is also portable. This is an easy-to-hold effect. By providing the bottom handle 729 at the front end of the bottom surface as well, the corner portion is gripped, and the ease of holding can be improved.

  In addition, although the recessed part 727 of the heat insulation box 701 comprised the right and left wall surface with the heat insulating body 715, if the side surface is comprised only by the shell 724, the heat dissipation of the compressor 711 will improve, and also the component space arrange | positioned in the recessed part 727 Can be taken big.

  In the present embodiment, the compressor 711 is provided in the recess 727 at the rear of the top surface of the heat insulation box 701. However, the top surface of the heat insulation box 701 is substantially flat without providing a recess or the like. Even in the case where the top surface portion is provided with the compressor 711, in the refrigerator of the type in which the evaporator 709 is below the compressor 711, similarly, when it is laid down by transporting the refrigerator or the like, the suction disposed below the compressor 711 Since oil is prevented from flowing out to the pipe 733, the evaporator 709, etc., the amount of oil in the compressor 711 can be secured and the oil surface height can be prevented from being greatly reduced, and the sliding portion of the compressor 711 can be prevented. The oil supply can be secured, and the risk of damage to the compressor 711 can be reduced.

(Embodiment 8)
FIG. 30 is a schematic cross-sectional view of the compressor mounted on the refrigerator in the eighth embodiment of the present invention, and FIG. 31 is a view of the interior of the compressor mounted on the refrigerator in the eighth embodiment of the present invention as viewed from above. is there.

  In the figure, the suction pipe 800 is arranged in the compressor 100 of the lower shell 801 so as not to extend into the compressor, and is disposed on the same plane as the inside of the shell, and is opposed to the suction port 802a of the suction muffler 802. It is arranged to do.

  The reason why the opening in the shell of the suction pipe 800 is arranged substantially on the same plane as the inner surface of the shell is that the structure is reduced in size by preventing physical buffering of the suction pipe 800 with respect to internal components in the shell. It is for aiming at.

  An electric element 803 having a rotor 803a and a stator 803b is elastically supported by a lower shell 801 via a support portion 805 having an elastic member, and a compression element is disposed above the electric element 803. 804 is arranged.

  The refrigerating cycle in which a compressor 100, a condenser (not shown), a decompressor (not shown), and an evaporator (not shown) are provided in this order to form a series of refrigerant channels has R600a as a refrigerant. An oil 810 made of mineral oil having a high mutual solubility with respect to R600a is enclosed in the compressor 100.

  As described above, in the compressor 100 of the type in which the electric element 803 is disposed below, the support portion 805 prevents the rotor 803a of the electric element 803 that rotates with the operation of the compressor 100 from being buffered with the oil 810. It is arranged in consideration of the height and mounting position.

  The compression element 804 is formed with a contact portion 820 having a certain clearance from the upper shell (not shown) or the lower shell 801.

  Next, details of the compressor 100 will be described below.

  The shaft 840 includes a main shaft portion 841 in which the rotor 803a is fixed by press-fitting or shrink fitting, and an eccentric portion 842 formed eccentric to the main shaft portion 841. The cylinder block 850 has a substantially cylindrical compression chamber 851 and a bearing portion 843 for supporting the main shaft portion 841 of the shaft 840 and is formed above the electric element 803.

  At this time, a rotor recess 803c is formed on the compression element 804 side of the rotor 803a, and a bearing portion 843 extends into the rotor recess 803c so that the compression element 804 is replaced with the rotor of the electric element 803. The size is reduced by being inserted within the height range.

  The piston 860 is loosely fitted in the compression chamber 851 and connected to the eccentric portion 841 of the shaft 840 by the connecting means 861. The rotational motion of the shaft 840 is converted into the reciprocating motion of the piston 860, and the piston 860 is in the space of the compression chamber 851. The refrigerant in the shell is sucked from the suction port 802a of the suction muffler 802 by enlarging and reducing the size of the discharge muffler 802, and a discharge muffler formed in the cylinder block 850 via a valve (not shown) provided inside the cylinder head 852. 853, the discharge pipe 854, and the discharge tube 870 are discharged to the discharge pipe 831 outside the shell.

  The discharge pipe 854, which is a high-pressure pipe, is a steel pipe having an inner diameter of 1.5 mm to 3.0 mm, and is formed so as to be flexible by using L-shaped or U-shaped bending. Are connected with elasticity.

  The electric element 803 uses an inverter motor using a permanent magnet for the rotor 803a. In conventional induction motors, torque required for operation of the compressor 100 is not generated unless the thickness of the stator 803b and the rotor 803a is large, but an inverter motor using a permanent magnet is used for the rotor 803a. By using it, the exciting current necessary for generating the rotational torque is not required, so that the thickness of the stator 803b and the thickness of the rotor 803a can be reduced, and the electric element 803 can be made compact.

  Next, the operation of the compressor 100 will be described.

  When the compressor is energized, current flows through the terminal 880 and the lead wire 881 to the stator 803b of the electric element 803, and the rotor 803a is rotated by the rotating magnetic field generated by the stator 803b. Due to the rotation of the rotor 803a, the eccentric portion 842 of the shaft 840 connected to the rotor performs a rotational motion that is eccentric from the axis of the shaft 840. The eccentric motion of the shaft 840 is converted into a reciprocating motion by the connecting means 861 connected to the eccentric portion 842, and becomes a reciprocating motion of the piston 860 connected to the other end of the connecting means 861, and the piston 860 is compressed into the compression chamber 851. The refrigerant is sucked and compressed while changing the internal volume.

  The capacity of the piston 860 that sucks and discharges during one reciprocation in the compression chamber 851 is referred to as a cylinder volume, and the cooling capacity changes depending on the size of the cylinder volume.

  Next, the case where the refrigerator is tilted by transportation or the like with the compressor stopped will be described.

When the compressor 100 is not operated for a long time, the R600a is liquefied to become a liquid refrigerant 890, and stored in the upper part of the oil 810 that is mineral oil having a specific gravity higher than that of the liquefied R600a. As a general-purpose refrigerant in which the liquid refrigerant is stored in the upper part of the oil in a state where the refrigerant is liquefied in this manner, the same applies to a combination of a CO ₂ refrigerant and ester oil or ether oil. On the other hand, for example, in the case of R134a and ester oil generally used as a conventional refrigerant, the vertical relationship between the oil and the liquid refrigerant is reversed, the liquid refrigerant is stored in the lower part, and the ester oil is stored in the upper part. The

  In the compressor 100 using the combination of the refrigerant and oil of the type in which the liquid refrigerant 890 is stored in the upper part of the oil 810 as in the present embodiment, when the compressor 100 is tilted, the inner wall surface of the lower shell 801 is almost the same. When the oil 810 stored in the lower part reaches the suction pipe 800 opened on the same surface, it easily flows out of the shell, so that the oil 810 inside the shell decreases and the oil surface height decreases. End up.

  When the oil level is lowered in this way, the amount of oil supplied to the sliding portion of the compression element 804 is reduced, and wear of the sliding portion may occur, which may reduce reliability. was there.

In the present invention against this problem, approximately about 1/2 refrigerating capacity per unit volume compared to R134a, is used R600a is smaller refrigerant to approximately 1/20 in comparison with the CO _2. Thus, in order to obtain the R134a or CO ₂ equivalent refrigerating capacity, approximately twice that of the cylinder volume to R134a, since increased to 20 times as compared with CO _2, the piston displacement amount The cylinder of the compressor It increases in proportion to the increase in volume. That is, increasing the volume flow rate per unit of refrigerant time increases, until the inside of the refrigeration system about twice that of R134a is the flow velocity in the pipe as it passes through the refrigerant, about 20 times as compared to CO ₂ Therefore, the oil 810 staying in the refrigeration system can be quickly returned to the compressor 100, and the shortage of oil in the shell can be prevented.

  In addition, regarding such a decrease in the oil level of the refrigerator due to the transportation of the refrigerator, the rotation speed of the compressor is commercialized for 5 minutes or more, which is at least half of about 10 minutes immediately after the compressor is turned on. When an inverter device that is driven at a rotational speed higher than the power supply frequency is used, the piston displacement of the compressor increases due to the high rotation speed, thereby increasing the flow velocity in the piping when the refrigerant passes through the refrigeration system. Therefore, the oil 810 staying in the refrigeration system can be returned to the compressor 100 more quickly, and an insufficient amount of oil in the shell can be prevented.

  Further, in the compressor 100 of the present embodiment, the compressor is downsized in the height direction, and the compressor of the present embodiment is compared with the total height of 190 to 200 mm of a conventional general small compressor. 100 is designed to be downsized in the height direction to about 145 mm.

  When miniaturizing the overall height of such a compressor, in order to avoid a decrease in reliability, the oil level of the amount of oil enclosed in the compressor is equivalent to that of a general conventional small compressor. Since the oil level of the conventional compressor is about 12 to 13% because the height of about 30 mm is secured, in the small compressor of the present embodiment, the oil with respect to the total height of the compressor. The oil level has increased to about 17%, and oil spilling when the compressor is tilted has become a bigger problem.

  In response to this problem, the compressor 100 of the present embodiment reduces the size of the compressor by reducing the height of the compression element 804 and the electric element 803 in order to reduce the size.

  That is, the portion of the support portion 805 that elastically supports the mechanical portion including the compression element 804 and the electric element 803 is not taken in as a height reduction element, and the mechanical portion of the compression element 804 and the electric element 803, that is, the internal components are high. By reducing the height, the oil 810 is not buffered with the electric element 803 of the machine unit, and the oil level height is less likely to vary.

  As described above, in the embodiment in which the compressor 100 is arranged at the upper part of the refrigerator main body, regarding the downsizing of the compressor 100 in the height direction, which is a big problem, the oil outflow is promoted particularly among the elements and viewpoints for downsizing. In other words, it employs a unique combination of the above-described miniaturization elements for maintaining reliability related to oil spill suppression.

  Further, the oil 810 can be prevented from flowing out by ensuring a dimensional relationship equal to or higher than that of the conventional compressor with respect to the height from the uppermost portion of the oil surface of the oil 810 to the opening of the suction pipe 800. For example, the opening position of the suction pipe 800 to the shell is located above the half height with respect to the maximum height in the shell, thereby preventing the oil outflow when the compressor 100 is inclined. Can be bigger.

  In the present embodiment, the compression element 804 is formed with a contact portion 820 having a certain clearance from the upper shell (not shown) or the lower shell 801. Since the portion 820 and the upper shell or the lower shell 801 are in contact with each other, the mechanical portion including the large compression element 804 and the electric element 803 is not greatly inclined. Therefore, it is possible to prevent the mechanical portion from compressing the volume of the oil moved to the inclined side and to secure a space portion, thereby preventing the oil 808 from easily flowing out from the suction pipe.

(Embodiment 9)
FIG. 32 shows a schematic cross-sectional view of a compressor mounted on the refrigerator in the ninth embodiment of the present invention.

  Inside the compressor 900, the suction pipe 906 extends into the shell, and is a direct suction type joined to the suction muffler 939 via a spring 906a that is an elastic member, and passes through the internal space path of the suction muffler 939. 936 leading into. Further, the inner side of the shell of the suction pipe 906 has a bent portion directed upward, and opens upward in the shell and is connected to a spring 906a which is an elastic member.

  In addition, the suction muffler 939 is connected to the cylinder head 935 and is disposed in the same direction as the cylinder 936 and the cylinder head 935. Further, the suction pipe 906 is also disposed in the same direction so as to be connected to the suction muffler 939. The discharge pipe 907 has a predetermined pipe length so as to increase the elasticity of the pipe to reduce pressure pulsation, and is attached to the lower shell on the side opposite to the cylinder head. By configuring the suction pipe 906 and the discharge pipe 907 on the opposite sides, a more compact compressor 900 can be configured.

  With the direct suction configuration as described above, even when the compressor 900 is inclined, a minute space such as a gap in the cylinder 936, a valve gap in the cylinder head 935, and an oil 908 return hole (not shown) provided in the suction muffler 939 is provided. Only through the oil 908, backflow outflow of oil 908 occurs.

  If the suction pipe 906 and the suction muffler 939 are joined by a tightly wound spring, the transmission of compression vibration is reduced, and the oil 908 can also reduce the outflow from the spring gap due to viscosity. It is possible to reduce the backflow.

  In this embodiment, a spring is used as an elastic member for connecting the suction pipe 906 and the suction muffler 939. However, an elastic resin such as rubber may be used.

  As described above, since the refrigerator according to the present invention can be used effectively and conveniently, the refrigerator can be applied to equipment using a cooling device such as a refrigerator for home use or business use.

Vertical sectional view of the compressor of the present embodiment Horizontal sectional view of the compressor of the present embodiment Comparison diagram of induction motor and inverter motor of compressor in Embodiment 1 Plan view of salient pole concentrated winding stator of compressor in the first embodiment The perspective view of the leg part of the compressor of the refrigerator in this Embodiment 1. Schematic sectional view of a refrigerator compressor according to Embodiment 2 of the present invention. Schematic sectional view of a refrigerator compressor according to Embodiment 2 of the present invention. Schematic sectional view of a compressor in Embodiment 3 of the present invention The schematic perspective view of the airtight container of the compressor in Embodiment 3 of this invention. Schematic plan view of an airtight container of a compressor in Embodiment 3 of the present invention Schematic sectional view of the compressor in the present embodiment Schematic sectional view of the refrigerator in the fourth embodiment of the present invention. Schematic rear view of the refrigerator in the same embodiment Schematic component development view of the refrigerator in the same embodiment Vertical sectional view of the compressor of the refrigerator in the same embodiment Horizontal sectional view of the compressor of the refrigerator in the same embodiment Comparison diagram of induction motor and inverter motor of refrigerator compressor in the same embodiment Top view of salient pole concentrated winding stator of refrigerator compressor in the same embodiment The perspective view of the leg part of the compressor of the refrigerator in the embodiment Schematic sectional view of the refrigerator in the fifth embodiment of the present invention. Schematic of the refrigerator in the sixth embodiment of the present invention Solubility curve diagram of refrigerant and refrigerating machine oil in the same embodiment Schematic sectional view of the refrigerator in the seventh embodiment of the present invention. Schematic rear view of the refrigerator in the same embodiment Schematic component development view of the refrigerator in the same embodiment Schematic perspective view of the main part of the suction pipe of the refrigerator in the same embodiment Schematic sectional view of the compressor mounted on the refrigerator in the same embodiment Schematic sectional view of the transport state of the refrigerator in the same embodiment Schematic sectional view of the compressor during refrigerator transportation in the same embodiment Schematic sectional view of a compressor mounted on the refrigerator in the eighth embodiment of the present invention. The figure which looked at the inside of the compressor carried in the refrigerator in Embodiment 8 of the present invention from the upper part Schematic sectional view of a compressor mounted on a refrigerator in Embodiment 9 of the present invention Schematic sectional view of a conventional refrigerator

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Box main body 11,601,711,900 Compressor 15a Door 15b Storage room 23,200 Top surface 27 Recessed part 28a Back surface 29a Top stage storage space 30c Indoor side bottom wall surface 30d Shelf bottom part 34b, 203 Top part 101 Lower container 102 Upper container 103 , 403 Sealed container 106 Leg 106b Adhering surface 106c Bending portion 106d Elastic member arrangement lower surface 107,270 Elastic member 110 Electric element 111,240 Rotor 111a Rotor recess 112 Stator 113,209 Compression element 130,210 Shaft 131,210b Main shaft Portions 132, 210a Eccentric portion 134, 231 Compression chamber 135 Bearing portion 136, 232 Piston 151 Permanent magnet 161 Stator core 171 Salient pole portion 201 Ventilation duct 202 Lower surface 210c Sub shaft portion 220 Main bearing 221 Sub bearing 280 Compaction installation surface 281 Depression 406 Leg 410 Cove part 410a Leg cove part 410b Support cove part 411 Concave cove part 413 Support member 413a Support part 420 Connection part 456 Leg 456a Adhering surface 609, 709 Evaporator 613 First top surface part 615 Second top surface 617 Machine room cover 618 Refrigeration cycle 619 Capillary 620 Suction line 701 Heat insulation box 727 Recessed portion 733 Suction piping 736 Oil outflow prevention trap 737 Piping U bent portion 738 Lower shell 739 Upper shell 740a Shell joint 740 Compressor shell 741 Elastic body 742 Rotation drive part 743 Compression part 744 Discharge piping 745 Oil 746 Support part 751 Eccentric shaft 752 Shaft 753 Bearing 754 Cylinder head 755 Cylinder 756 Piston 75 Rod 758 sliding unit 800 suction piping 801 the lower shell 803 motor element 803a rotor 803b stator 804 compression element 805 supporting portion 810 oil 843 bearing portion 906 suction pipe 906a spring 907 discharge pipe 908 oil 935 cylinder head 936 cylinder 939 suction muffler

Claims (10)

  An electric element composed of a stator and a rotor and a compression element driven by the electric element are housed in a hermetic container, and a leg of the compressor is fixed to the hermetic container and the leg of the compressor Is elastically supported via an elastic member with respect to the installation surface of the compressor, and the mechanical portion composed of the compression element and the electric element is elastically supported via a support member with respect to the sealed container. The compression element is a reciprocating type including a compression chamber, a piston that reciprocates in the compression chamber, and a shaft having a main shaft portion and an eccentric portion, and the rotation fixed to the main shaft portion. A rotor and a bearing portion that pivotally supports the main shaft portion, the rotor has a rotor recess on the compression element side, and the bearing portion extends into the rotor recess, and the electric element Inverter motor operated at multiple speeds Further, by using a permanent magnet for the rotor of the electric element, the height of the mechanical part is reduced, and the contact surface between the leg of the compressor and the elastic member is placed under the support member. A compressor with a reduced height by positioning it above the end face.   The distance between the center of gravity of the compressor in the vertical direction and the contact surface between the legs of the compressor and the elastic member is shorter than the distance between the center of gravity of the compressor in the vertical direction and the lower end surface of the support member. The compressor described in 1.   The compressor according to claim 1 or 2, wherein the height of the elastic member is larger than the distance between the installation surface and the lowest part of the sealed container.   The compressor leg according to any one of claims 1 to 3, wherein the legs of the compressor have a fixing surface that is fixed to the sealed container, a bent portion that rises upward, and a contact surface that locks the elastic member.   The compressor according to claim 4, wherein the legs of the compressor are provided with ribs extending across at least two places of the fixing surface, the bent portion, and the contact surface.   The compression element according to any one of claims 1 to 5, wherein the electric element is a salient pole concentrated winding type in which a winding is wound through a plurality of salient pole part insulators of a stator core constituting the stator. Machine.   The compression element includes a cylinder block having a compression chamber, the cylinder block includes a leg portion that forms a mounting surface to the electric element, and the leg portion of the cylinder block is connected to the salient pole concentrated winding type stator core. The compressor according to claim 6, wherein the length of the block leg portion is shortened by being attached.   The compressor according to any one of claims 1 to 7, wherein the permanent magnet housed in the rotor is a rare earth permanent magnet.   The compressor according to any one of claims 1 to 8, wherein a height from a lower end portion of the sealed container to a top portion of the sealed container is 144 mm or less.   A refrigeration apparatus having a refrigeration cycle that includes the compressor according to any one of claims 1 to 9, a condenser, a decompressor, and an evaporator in order to form a series of refrigerant flow paths.

Images