JP4720936B2 - Compressor for refrigerator - Google Patents

Description

  The present invention relates to a refrigerator that realizes a power saving operation that is more energy saving.

  As a conventional refrigerator, there is a refrigerator related to a power-saving operation according to a detection amount detected by an optical sensor, a door SW, or the like. When the optical sensor detects a predetermined illuminance or more, a normal operation is performed, When it is detected that the illuminance is below, the customer is likely to go to bed and open the refrigerator door, so there is a product that performs power-saving operation that is operated with less power than normal temperature.

  Moreover, even when the customer goes to bed with some of the lights turned on, the power saving operation is performed (see, for example, Patent Document 1).

  A front view of the refrigerator is shown in FIG. 27, an example of an electric circuit diagram is shown in FIG. 28, and an explanatory diagram of an operating state of the refrigerator using the electric circuit is shown in FIG.

  In the figure, a refrigerator 1 includes a refrigerator compartment door 2, a vegetable compartment door 3, an ice making compartment door 4, a switching compartment door 5, and a freezer compartment door 6 on the front side of the storage compartment. The operation unit 7 includes various operation switches (not shown), a liquid crystal display unit 8, and an optical sensor storage unit 9.

  Optical sensor 10 for detecting the illuminance around the refrigerator, resistor 11, AD converter 12 for converting the input analog voltage value to a digital signal, and memory for storing the signal from the AD converter The device 13 is a microcomputer 14 that is a control device for inputting signals from the AD converter and controlling the operation of a compressor (not shown). The operation of the compressor is mainly ON / OFF controlled by a freezer sensor (not shown).

  The microcomputer 14 operates as described below.

  When a switch (not shown) for enabling power saving operation is pressed, the optical sensor 10 detects the illuminance around the front side of the refrigerator (S1). Then, the change rate of illuminance is calculated (S2). The change rate of illuminance is calculated by dividing the change in illuminance by the time of change, and is, for example, 150 lux / second when there is a change of 150 lux per second. 150 lux / second is set as the predetermined change rate. However, it is considered that this set value may be set in the range of 100 to 200 lux / second.

  The rate of change is calculated, and it is determined whether this rate of change is equal to or greater than the set value, that is, 150 lux / second (S3). If the rate of change is equal to or greater than the set value, normal operation is performed (S4). If not, it is determined whether the decrease rate is equal to or greater than a set value (S5). If the decrease rate is equal to or greater than the predetermined value, power saving operation is performed (S6), and if the decrease rate is not equal to or greater than the set value, the illuminance detection in S1 is performed again.

  The operation for controlling the set temperature of the freezer (usually −20 ° C., the set temperature can be changed) to the set temperature is the normal operation, and the freezer compartment temperature is set to the set temperature (−20 ° C.). The power-saving operation is controlled to be a temperature close to 2 ° C. room temperature (−18 ° C.). For this reason, in this power saving operation, the operation time of the compressor becomes shorter than that in the normal operation, and the operation stop time becomes longer, so that power can be saved as compared with the normal operation.

According to the refrigerator configured as described above, the operation is as follows. For example, at around night 11, the user tries to go to bed and turns the light down. For example, it is assumed that one 20W fluorescent lamp is turned on and one 20W is turned on to sleep. Since the microcomputer calculates the decrease rate of the illuminance at this time and determines that the decrease rate is equal to or higher than a predetermined value, the power-saving operation is started in the refrigerator.

  In the refrigerator controlled in this way, since the refrigerator is controlled so that it can be saved even when it is dimmed, the conventional control in which the normal operation and the power saving operation were performed at or below a predetermined illuminance. Can save more energy.

JP 2002-107025 A

  However, in the above conventional configuration, when performing power saving operation, the compressor operation time is shorter than normal operation and the operation stop time is longer and the refrigerator can save power than normal operation. Because power saving is focused on the operation and stop times, the power required at the time of switching from the stop to the start of operation is large, so power saving beyond a certain level cannot be realized. Had.

  Also, in recent years, an inverter-driven compressor capable of driving at a plurality of rotation speeds capable of realizing power saving operation as compared with a compressor operating at a constant rotation speed with the above-described conventional configuration has also been developed in recent years. Is installed in a refrigerator for home use, but it was not envisaged to perform further power-saving operation with this inverter-driven compressor.

  This invention solves the said conventional subject, and it aims at providing the refrigerator which implement | achieved more energy saving by performing a power-saving operation further using a power-saving type inverter drive compressor in a refrigerator. .

In order to solve the above-described conventional problems, the refrigerator of the present invention is provided with a heat insulating box, the heat insulating box, and a series of refrigerant flow paths including a compressor, a condenser, a decompressor, and an evaporator in order. A compressor provided in a refrigerator having a refrigeration cycle formed and a control means for controlling the operation of the refrigeration cycle, wherein the compressor is an electric element comprising a stator and a rotor in a sealed container And a compression element driven by the electric element. The compression element is provided in the compression chamber, a piston that reciprocates in the compression chamber, a shaft having a main shaft portion and an eccentric portion, and the shaft. A reciprocating type having a crank weight , and the electric element includes an inverter electric motor operated at a plurality of rotation speeds including a rotation speed lower than a rotation speed of a commercial power source, and a piston reciprocates in the compression chamber. To move In forming a cylinder volume in which compression operation is performed me, than the horizontal line passing through the upper end of the piston with the piston during the compression operation is to increase the diameter of the piston than the stroke is the distance the reciprocating At least a part of the crank weight is located on the lower side .

  As described above, the present invention focuses on the cylinder volume of the compressor, and the compressor performs the operation in the energy saving mode which is the power saving operation after the energy saving in the inverter compressor. In addition, by using a compressor having a large cylinder capacity, it is possible to achieve both power-saving operation in the energy saving mode and high-capacity cooling in the high load cooling mode.

Furthermore, when using a compressor having a large cylinder volume as described above, the present invention focuses on the correlation between the diameter and stroke of the piston that forms the cylinder volume of the compressor. A compressor with high reliability can be realized even when operating at a wide range of speeds by forming a large cylinder volume by increasing the diameter of the piston instead of forming a large cylinder volume by lengthening It is possible to achieve both power saving operation in the energy saving mode and high capacity cooling in the high load cooling mode, and reduce the unbalance amount of the piston that increases due to the large piston diameter. Therefore, by providing a crank weight that extends downward from the upper end surface of the piston, the amount of unbalance accompanying the reciprocating motion of the piston is reduced, and vibration is suppressed. It is possible to realize a dependable high compressor.

  The refrigerator according to the present invention can achieve significant power saving in the actual refrigerator and can provide a refrigerator that realizes further energy saving.

Front view of the refrigerator in Embodiment 1 of the present invention The longitudinal cross-sectional view of the refrigerator in Embodiment 1 of this invention Front view of operation board of refrigerator in embodiment 1 of the present invention Front view of another type of operation board according to Embodiment 1 of the present invention Sectional view of the AA 'part of FIG. 2A Control block diagram according to Embodiment 1 of the present invention 1 is a longitudinal sectional view of a compressor mounted in Embodiment 1 of the present invention. The figure which shows the result which put together the rotation speed and refrigerating capacity of the compressor in Embodiment 1 of this invention for every cylinder volume. The figure which shows the result which summarized the number of revolutions and mechanical loss for each cylinder volume The figure which shows the relationship between the refrigerating capacity and COP put together for each cylinder volume The figure which shows the past reference data with respect to the arbitrary 1st in Embodiment 1 of this invention. Control flowchart according to Embodiment 1 of the present invention Good night control flowchart in Embodiment 1 of the present invention Flowchart of outing control in Embodiment 1 of the present invention Effect image diagram according to Embodiment 1 of the present invention Front view of the refrigerator in Embodiment 2 of the present invention Sectional drawing of the compressor in Embodiment 2 of this invention The perspective view of the crank weight of the compressor in Embodiment 2 of this invention Enlarged view around the crank weight of the compressor in the reference example Assembly drawing around elastic member of compressor in embodiment 2 of the present invention Sectional drawing of the elastic member periphery of the compressor in Embodiment 2 of the present invention The perspective view seen from the upper surface of the cylinder block of the compressor in Embodiment 2 of this invention The perspective view seen from the downward side of the cylinder block of the compressor in Embodiment 2 of this invention Plan sectional drawing of the suction tube periphery of the compressor in Embodiment 2 of this invention Vertical sectional view around the suction tube of the compressor according to Embodiment 2 of the present invention Vertical sectional view of a hermetic compressor according to Embodiment 3 of the present invention Main part longitudinal cross-sectional view of the compression part in Embodiment 3 of this invention Schematic diagram illustrating the behavior of the piston in the third embodiment of the present invention Characteristic diagram according to the fourth embodiment of the present invention Is an enlarged view of elements around the piston used in the hermetic compressor according to the embodiment. Top view of piston used for hermetic compressor in the fourth embodiment Front view seen from direction B in FIG. Top view of piston used for hermetic compressor in the fourth embodiment Front view seen from direction C in FIG. Top view of piston used for hermetic compressor in the fourth embodiment Front view of conventional refrigerator Electric circuit diagram of main parts of conventional refrigerator Typical flowchart of conventional refrigerator

According to a first aspect of the present invention, there is provided a heat insulating box, a refrigeration cycle disposed in the heat insulating box and including a compressor, a condenser, a decompressor, and an evaporator in order to form a series of refrigerant flow paths, and the refrigeration A compressor provided in a refrigerator having a control means for controlling the operation of a cycle, wherein the compressor is in a hermetically sealed container, an electric element comprising a stator and a rotor, and a compression driven by the electric element The compression element includes a compression chamber, a piston reciprocating in the compression chamber, a shaft having a main shaft portion and an eccentric portion, and a reciprocating motion having a crank weight provided in the shaft. The electric element includes an inverter electric motor operated at a plurality of rotation speeds including a rotation speed lower than the rotation speed of a commercial power source, and a compression operation is performed by reciprocating a piston in the compression chamber. Cylinder volume When formed, at least a portion of the crank weight downward from the horizontal line passing through the upper end of the piston with the piston during the compression operation is to increase the diameter of the piston than the stroke is the distance the reciprocating Is located .

  As described above, the present invention focuses on the cylinder volume of the compressor, and the compressor is operated in the energy saving mode, which is a power saving operation, while saving energy in the inverter compressor. In addition, by using a compressor having a large cylinder capacity, it is possible to achieve both power-saving operation in the energy saving mode and high-capacity cooling in the high load cooling mode.

Furthermore, when using a compressor having a large cylinder volume as described above, the present invention focuses on the correlation between the diameter and stroke of the piston that forms the cylinder volume of the compressor. A compressor with high reliability can be realized even when operating at a wide range of speeds by forming a large cylinder volume by increasing the diameter of the piston instead of forming a large cylinder volume by lengthening it can be, reduce high der one capable of both cooling and capacity is, imbalance of the piston to be increased by the diameter of the piston is large in power-saving operation and high-load cooling mode in energy-saving mode In order to reduce the unbalance amount associated with the reciprocating motion of the piston, the vibration is suppressed by providing a crank weight extending from the upper end surface of the piston to the lower side. It is possible to realize a dependable high compressor.

  As described above, in order to realize energy saving, the present invention uses a compressor having a large cylinder volume in the case of operation in an energy saving mode that is a power saving operation after achieving energy saving in an inverter compressor. In addition, power is saved by operating at low speeds, and when high loads occur due to door opening / closing or rise in the internal temperature, operation at high speeds can be shortened by using a compressor with a large cylinder volume. By performing it in time, it becomes possible to cope with a high load, and it is possible to realize a compressor that achieves significant power saving in the refrigerator.

  In addition, when a high load is applied, high load cooling is performed by controlling the electric element to be in a high load cooling mode that operates at a rotational speed greater than the rotational speed of the commercial power supply with a relatively large cylinder volume. Therefore, it is possible to quickly return from the high load cooling mode to the energy saving mode.

  In addition, since it is possible to operate at a lower speed by being able to operate at a rotational speed that is 1/2 or less of the rotational speed of the commercial power supply, significant power savings can be achieved in the actual refrigerator. Thus, it is possible to provide a compressor for a refrigerator that realizes further energy saving.

According to a second aspect of the present invention, the piston A is configured such that the relationship between the stroke A, which is the distance that the piston reciprocates during the compression operation, the length B of the piston, and the diameter C of the piston satisfies A ≦ B ≦ C. This is a compressor for a refrigerator that increases the diameter of the refrigerator.

  As a result, when using a compressor having a large cylinder volume, the correlation between the piston diameter and stroke that form the cylinder volume of the compressor, and the piston diameter and piston length are emphasized. Yes, instead of forming a large cylinder volume by increasing the stroke, a large cylinder volume is formed by increasing the diameter of the piston, and the load associated with reciprocation is reduced by further reducing the length of the piston. Therefore, it is possible to realize a compressor with high reliability even when operating at a wide range of rotation speeds. Power saving operation in the energy-saving mode and high-capacity cooling in the high-load cooling mode can be achieved. It can be compatible.

According to a third aspect of the invention, the direction in which the piston reciprocates during the compression operation is a horizontal direction, and the compression for the refrigerator has a piston diameter of 19% to 38% with respect to the total height of the compressor. Machine.

  As described above, when the present invention is mounted on a large-capacity refrigerator that increases the internal capacity by lowering the overall height of the compressor, it is normal to lengthen the stroke to reduce the overall height of the compressor. In spite of its simple structure, the focus is on enlarging the piston diameter, and it is highly reliable even when operating at a wide range of speeds. Therefore, it is possible to achieve both a power saving operation in the energy saving mode and a high capacity cooling in the high load cooling mode.

According to a fourth aspect of the present invention, there is provided a mechanical part including a compression element and an electric element via a spring which is an elastic member in the sealed container, the holding part provided at the bottom of the sealed container, and the machine The structure is such that the spring and the support part are more easily removed in the vertical direction than the spring and the holding part, that is, with a small load, and elastically supported by the spring between the support part and the support part. According to a fifth aspect of the present invention, there is provided a mechanical part including a compression element and an electric element via a spring which is an elastic member in the sealed container, and the holding part provided at the bottom of the sealed container. The portion that is elastically supported by the spring between the support portion and the support portion that supports the mechanical portion, and that is not in contact with the spring during steady operation when a lateral load is applied In which is provided a small gap than the holding portion in a radial direction relative to the said than holding portion toward the support portion is likely to collide with the spring i.e. the spring the supporting part in.

Thus, according to the present invention, the spring, which is an elastic member, has a smaller fit when pressed in the longitudinal direction, so that the loose fit is achieved. Even when a piston with a large diameter is used, the spring is compressed through the sealed container. Vibration transmitted to the outside of the machine can be suppressed, while the lateral direction has a small gap and is harder to move, and this radial (ie, horizontal) gap functions as a buffer that suppresses contact with the hook. By doing so, it is possible to suppress the phenomenon of hook contact associated with the start and stop of the machine part, and it is possible to provide a highly reliable compressor having a large cylinder capacity.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the drawings. The same reference numerals are given to the same configurations as those of the conventional example or the embodiments described above, and detailed descriptions thereof will be omitted. The present invention is not limited to the embodiments.

(Embodiment 1)
1A is a front view of the refrigerator according to Embodiment 1 of the present invention, FIG. 1B is a sectional view of the refrigerator according to Embodiment 1 of the present invention, and FIG. 2A is a configuration of an operation board of the refrigerator according to Embodiment 1 of the present invention. FIG. 2B is a configuration diagram of an operation board of another form of the refrigerator according to Embodiment 1 of the present invention. 3 is a cross-sectional view of the AA ′ portion of FIG. 2A, FIG. 4 is a control block diagram, FIG. 5A is a cross-sectional view of a compressor mounted in the first embodiment of the present invention, and FIG. 6 is the first embodiment of the present invention. FIG. 7 to FIG. 9 are control flowcharts according to Embodiment 1 of the present invention, and FIG. 10 is an effect image diagram according to Embodiment 1 of the present invention.

  In FIG. 1A, the heat insulation box which is the refrigerator main body 21 has a refrigerated room 22, an ice making room 23, a switching room 24, a freezer room 25, and a vegetable room 26 in order from the top. An operation unit 27 is disposed in the vicinity of the center of the refrigerator compartment door 22a of the refrigerator compartment 22, and an operation substrate 27a is formed inside the operation unit 27. The illumination intensity is above the vertical axis extension line of the operation substrate 27a and upward. An illuminance sensor 36 serving as detection means is provided. The illuminance sensor 36 can be specifically configured by using an optical sensor having a photodiode or phototransistor as a base element.

  The operation board 27a has an operation switch 37 for setting the internal temperature of each room, ice making, rapid cooling, and the like, an indicator lamp 38 for displaying a state set by the operation switch, and detection of an illuminance sensor 36. Thus, the notifying means 39 using an LED or the like for notifying the variable operating state of the refrigerator is configured.

  In front of the illuminance sensor 36, an illuminance sensor cover 41 in which a part of the operation unit cover is substantially transparent is configured to detect light in the refrigerator installation environment by the illuminance detection means. An LED cover 42 for transmitting light emission is formed on the front surface, and these covers are formed on an operation board cover 43.

  Furthermore, the layout of the door is representative and is not limited to this layout.

  In the figure, the heat insulating box which is the refrigerator main body of the refrigerator 21 is foam filled in the outer box mainly using a steel plate, the inner box molded with a resin such as ABS, and the space between the outer box and the inner box. It is comprised with the foaming heat insulating materials, such as hard foaming urethane, and is thermally insulated with the circumference | surroundings and is heat-insulated by the partition wall in the several storage chamber. A refrigerating room 22 is provided at the top, a switching room 24 or an ice making room 23 is provided side by side at the bottom of the refrigerating room, a freezing room 25 is disposed at the bottom of the switching room 24 and the ice making room 23, and a vegetable room 26 is disposed at the bottom. In addition, a door is formed in the front opening of the refrigerator main body in order to partition outside air from the front of each storage room.

  The refrigerator compartment 22 is normally set to 1 ° C. to 5 ° C. at the lower limit of the temperature at which it does not freeze for refrigerated storage, and the lowermost vegetable compartment 26 is set to 2 ° C. to 7 ° C., which is the same or slightly higher temperature setting as the refrigerator compartment 22. In addition, the freezer compartment 25 is set in a freezing temperature zone and is usually set at −22 ° C. to −15 ° C. for frozen storage, but for example, −30 ° C. or − It may be set at a low temperature of 25 ° C.

  The switching chamber 24 is not only refrigerated set at 1 ° C to 5 ° C, vegetables set at 2 ° C to 7 ° C, and frozen at a temperature set usually at -22 ° C to -15 ° C. It is possible to switch to a preset temperature range between the freezing temperature ranges. The switching room 24 is a storage room provided with an independent door arranged in parallel with the ice making room 23, and is often provided with a drawer-type door.

In the present embodiment, the switching chamber 24 is a storage room including the temperature range of refrigeration and freezing. However, the refrigeration is performed by the refrigeration room 22 and the vegetable room 26, and the freezing is performed by the freezing room 25. A storage room specialized for switching only the temperature zone in the middle of the freezing may be used. Moreover, the storage room fixed to refrigeration may be sufficient as the demand for frozen foods has increased in recent years, for example, frozen food.

  The ice making chamber 23 makes ice with an automatic ice maker (not shown) provided in the upper part of the room with water sent from a water storage tank (not shown) in the refrigerator compartment, and an ice storage container (not shown) arranged in the lower part of the room. To store).

  The top surface of the heat insulating box has a stepped recess in the rear direction of the refrigerator. A machine room is formed in the stepped recess, and the compressor 28 and water are removed from the machine room. Houses high-pressure components of the refrigeration cycle such as a dryer (not shown). That is, the machine room in which the compressor 28 is disposed is formed by biting into the uppermost rear region in the refrigerator compartment 22.

  In this embodiment, the matters relating to the main part of the invention described below are of the type in which a compressor room is provided by providing a machine room in the rear region of the lowermost storage room of a heat insulation box that has been generally used conventionally. You may apply to the refrigerator 21. FIG.

  A cooling chamber 29 for generating cold air is provided on the back surface of the freezer compartment 25 and is partitioned from an air passage. Between these air passages, a cool air carrying air passage to each chamber having heat insulation properties, and each storage chamber is insulated. A rear partition wall configured to partition is configured. In addition, a partition plate for separating the freezing chamber discharge air passage and the cooling chamber 29 is provided. A cooler 30 is disposed in the cooling chamber, and in the upper space of the cooler 30, cold air cooled by the cooler by a forced convection method is blown to the refrigerating room, the switching room, the ice making room, the vegetable room, and the freezing room. A cooling fan 31 is disposed.

  Further, a radiant heater 32 made of glass tube is provided in the lower space of the cooler 30 for defrosting the frost and ice adhering to the cooler 30 and its surroundings at the time of cooling. A drain pan for receiving defrosted water, a drain tube penetrating from the deepest part to the outside of the warehouse is configured, and an evaporating dish is configured outside the downstream side of the warehouse.

  The compressor 28 accommodates an electric element 110 including a rotor 111 and a stator 112 and a compression element 113 driven by the electric element 110 in an airtight container 103. The compression element 113 is compressed with a compression chamber 134. It is an electric motor of an inverter that is reciprocating with a piston 136 that reciprocates in the chamber 134 and that is operated at a plurality of rotational speeds including a rotational speed lower than that of a commercial power source.

  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 sealed container 103 and is provided in the refrigerator via an elastic member.

  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.

  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 eccentrically 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.

  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. Is expanded and reduced to compress the refrigerant 104 in the sealed container 103 and discharge it to the refrigeration cycle.

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

  In the rotor 111, a main body portion in which silicon steel plates of 0.2 mm to 0.5 mm are stacked and a permanent magnet provided on the main body portion are integrally fixed.

  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 is a salient pole concentrated winding type in which salient pole portions are formed in an annular shape at predetermined intervals, and a winding 162 is wound around the salient pole portions. Each winding is connected to one by a connecting line.

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

  In conventional refrigerators, temperature control is performed to meet the set temperature regardless of day or night, but at night, the ambient temperature of the refrigerator decreases, the heat load decreases, and food is removed or replaced. Since the heat load generated when doing so becomes extremely small, the refrigerator internal temperature becomes a slightly supercooled temperature setting. In addition, energy-saving means using conventional optical sensors could not achieve energy-saving effects unless their functions were activated using dedicated buttons such as “Power-saving mode”.

  The present invention achieves energy saving without pressing a dedicated button, that is, with an auto function. That is, the illuminance sensor 36 attached to the front surface of the refrigerator body 21 detects the illuminance level around the refrigerator due to solar radiation or irradiation of indoor lighting equipment, and at the same time, detects the temperature of each storage room and is cooled below a specified temperature. In addition, if the past door opening / closing status is input to the control means, and if it is smaller than a predetermined value, it is determined that there is no activity at night or humans, and the cooling performance of the refrigerator is automatically reduced slightly. Switch to mode. When the illuminance level becomes larger than the specified value, the operation is returned to the normal mode. However, since the instantaneous light emission from the outside, for example, detection by lighting of an automobile or the like is excluded, the power saving mode is not canceled unless the illuminance level continued to some extent is maintained.

  Furthermore, past illuminance, door opening / closing, and internal temperature are stored in a delimiter storage means in a certain unit of time, and the operation of the refrigerator is controlled by determining the pattern.

  Further, when the power saving operation is started, the notification means, for example, the LED is turned on to appeal the situation to the user.

  At this time, if the light receiving surface of the illuminance sensor 36, that is, the illuminance sensor cover 41 is blocked by something, accurate illuminance detection becomes impossible, and switching to the power saving mode and returning to the normal mode cannot be performed. In general, as a factor for shielding light, it is conceivable that a paper surface or the like is attached to the surface of the refrigerator compartment door 22a. However, in the present embodiment, since the illuminance detection means 8 is installed above the vertical axis of the operation board 7, which is very unlikely to be pasted, erroneous illuminance detection is not performed. Although not shown in the figure, the failure can be further prevented by alerting the user by describing its presence in the vicinity of the illuminance sensor.

  Next, description will be made with reference to the control block diagram of FIG.

  Depending on the installation environment of the refrigerator and its use, the detection means for detecting the ambient environment around the refrigerator installation environment, the illuminance detection means for detecting the illuminance, the human sensor 40, the state detection means for detecting the use status of the refrigerator, the door SW51, the outside air temperature A plurality of sensors such as the sensor 52 and the internal temperature sensor 53 are mounted.

  In the refrigerator of the present invention, the illuminance sensor 36 detects the light and darkness around the front surface of the refrigerator, outputs it to the control means 54, and further stores the data in the storage means 55. Similarly, the number of doors opened and closed, the door opening and closing time, the outside air temperature sensor provided in the outer casing of the refrigerator, and the temperature inside each box are detected by the output signal of the door SW51 that detects the open / close state of the refrigerator door 22a and other doors. Temperature data detected by the internal sensor is also input to the storage means.

  This data is taken out at regular intervals, and an operation pattern is set by the control means 54, and the temperature setting of the compressor 28, the cooling fan 31, the temperature compensation heater 56, and each storage chamber is automatically varied. Here, if it is detected by the illuminance sensor 36 that it is 5 Lx or less, and the state has passed for a certain period of time and further cooled to a predetermined temperature or less, power saving such as suppression of compressor rotation speed and overcooling prevention operation is performed. The system automatically enters operation and turns on or blinks the LED as a notification means for a certain period of time.

  Details of these operations will be described with reference to the control flow diagram of FIG.

  When the power is turned on in step 1101 in the refrigerator, a timer T for measuring the constant interval A is started in step 1102 and control is started in step 1103 in the main flow for operating a normal refrigerator. At this time, if there is door opening / closing in step 1104, the door opening / closing number M is counted in step 1105.

  Next, if the detection of the illuminance sensor in step 1106 is, for example, 5 Lx or more, normal operation is continued. However, detection of 5 Lx or less is detected, and as shown in steps 1107, 1108, and 1109, the illuminance detected by the illuminance sensor continues for 5 minutes or more. When the storage room temperature is cooled below the specified temperature and it is determined that the door has not been opened and closed for the past 10 minutes, the process shifts to a sleep control flow that is an energy saving mode shown in FIG.

  If the timer T reaches the predetermined interval A in step 1111, the door opening / closing number or door opening / closing time and average illuminance until that time are calculated and stored in the storage means in step 1112.

  Then, the door opening / closing number, illuminance data, etc. are initialized, and the door opening / closing number and illuminance are again measured for the next hour, for example.

  Next, the night control shown in FIG. 8 will be described.

  When entering sleep control, which is an energy-saving mode, it is predicted that the patient will go to bed, and the refrigerator load due to opening and closing of the door can be predicted to be much less than normal, and the state is predicted to continue for a long time, for example, 6 hours. Can save energy.

  Specifically, as described in step 1121, the food loading load and the door opening / closing load are small, so that the refrigerator internal temperature setting can be set higher by about 1K to 2K, and the temperature behavior in the refrigerator is slowed down. This creates an energy saving effect. At this time, the compressor and the cooling fan are operated at a low speed to achieve an energy saving effect and a low noise. Furthermore, the input of the temperature compensation heater can be reduced by increasing the internal temperature control setting.

  Thereafter, if there is no change in the door opening / closing detection in step 1122, the illuminance detection in step 1124, and the internal temperature detection in step 1126, the mode is maintained.

  If even one of the above changes, the mode maintenance determination is performed.

  Specifically, if door opening / closing is detected in step 1122, the process proceeds to step 1123, and if it is determined that the number of door opening / closing is N1 times or more set in advance, the sleep control is canceled as in step 1127. Then, the control shifts to the normal control which is the normal cooling mode. Similarly, if the illuminance sensor detects 10 Lx or more in step 1124, the process proceeds to step 1125, and if the illuminance sensor detects 10 Lx or more continuously for 5 minutes or more, the process proceeds to step 1127 and the sleep control is canceled.

  Next, the outing control as an example of the energy saving mode will be described with reference to FIG.

  A going-out control determination is performed in step 140 at regular intervals during execution of step 1103, for example, every 24 hours.

  First, determination is made at Step 1142 using the door opening / closing number, illuminance, and internal temperature data for the past three weeks stored in the storage means of Step 1141.

  For example, if the door has not been opened and closed for 3 hours or more in the same time zone in the past 3 weeks in step 1143, the lifestyle pattern of this family is absent during the day due to, for example, working together. In step 1144, if each storage room is sufficiently cooled, or if the door has not been opened / closed in step 1145 for the past 10 minutes, it enters outing control as in step 1146, and as described in step 1147, the energy saving mode is determined. Implement energy-saving operation. However, unlike the night control described with reference to FIG. 6, it is also assumed in the daytime, so the temperature rise is suppressed to 0.5K to 1K than the night control. About other things, the control almost equivalent to the sleep control is performed.

  Therefore, when the energy saving control as shown in the flowchart of the figure is performed, the temperature behavior as shown in FIG. 10 is obtained, and the energy saving operation is achieved.

  Next, the operation of the compressor 28 will be described.

  When the compressor 28 is energized, electricity is supplied to the stator 112 of the electric element 110, 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.

  Specifically, the engine is operated at a plurality of preset rotation speeds such as six stages such as 20 rps, 28 rps, 35 rps, 48 rps, 58 rps, and 67 rps. Further, among the multiple stages of rotation speeds, there are at most two that are larger than the rotation speed of the commercial power supply, and more than half are rotation speeds smaller than the rotation speed of the commercial power supply.

In a refrigerator equipped with this inverter compressor, it is possible to operate at a low rotation of 1/3 of 60 Hz, which is a frequency of a general commercial power supply, such as a low rotation operation in a power saving operation and a rotation speed of 20 rotations / s, The rotation speed was set to 28 rotations / s, which is a lower rotation speed than 1/2 of the commercial power source.
In sleep mode, the number of revolutions is 30 rev / s. Similarly, in the energy saving mode, higher illuminance is detected than in sleep control, so the outing mode determined to be within the user's activity time. In this case, the rotation speed was 35 revolutions / second.

  In the normal cooling mode, which is the normal cooling mode, the rotation speed is set to 35 rpm / center and 48 rps at the maximum, which is lower than the rotation speed of commercial power in Japan.

  Further, the rotation speed of commercial power supply in Japan is 50 rotations / s or 60 rotations / s. However, in this embodiment, the rotation speed of a higher commercial power supply is 60 rotations / s, which is the rotation speed of a general commercial power supply. It was.

  The rotation speed of 60 rotations / s or more is used only when a high load is applied due to a rapid temperature rise caused by opening and closing the door.

  In the present embodiment, in the refrigerator equipped with this inverter compressor, in the sleep mode that is the energy saving mode as described above, the main rotation speed is 30 rotations / s, and similarly in the energy saving mode, the case of the sleep control In comparison with the high illuminance, the main rotation speed was set to 35 rotations / s in the outing mode determined to be within the user's activity time.

  As described above, in addition to the energy-saving mode, which is a power-saving operation, the compressor achieves further power saving by operating at a lower speed than the rotational speed of the commercial power supply in the normal cooling mode during normal operation as well as high load. By controlling the electric element to be in a high-load cooling mode that operates at a speed higher than the rotational speed of the commercial power supply only when it is applied, energy saving and normal cooling, which is 80% or more when the refrigerator is used annually By focusing on the mode and rotating the compressor at a low rotation, it is possible to achieve a significant power saving in the actual refrigerator and to provide a refrigerator that realizes further energy saving.

  In addition, when operating in an energy saving mode in which the frequency of use of the refrigerator of these users is expected to decrease, the rotation speed of the compressor is set in advance including the rotation speed A lower than the rotation speed of the commercial power source. If the illuminance sensor detects a specified value or more in the state where the engine is operated in the energy saving mode of the rotational speed A, the rotational speed A operated at that time is detected. It is assumed that the engine is operated at a rotation speed B that is higher than the rotation speed A and has the smallest difference in rotation speed from the rotation speed A.

  For example, when the compressor is operating at 30 rev / s (rotation speed A) as a sleep mode, even if the ambient illuminance increases and the illuminance sensor detects a high illuminance that exceeds a specified level, The number of rotations is not increased to 35 rotations (number of rotations A), but the number of rotations is higher than 30 rotations / s (number of rotations A) and the difference in number of rotations from 30 rotations / s (number of rotations A) is the smallest. The control is such as driving in B).

  Thus, when high illuminance is detected by the illuminance sensor, that is, when it is detected that it is the activity time of the refrigerator user, it is assumed that the load is actually applied by opening and closing the refrigerator, As a corresponding preparatory stage, the number of revolutions is gradually increased to prevent overloading and energy conservation is achieved, and even when high loads such as door opening and closing are actually applied, high rotation speed is achieved quickly. It is possible to shift to the high-load mode that operates by the number, so that energy saving can be realized and the high-load mode of the refrigerator can be handled with improved compressor reliability, and power saving in the energy-saving mode is possible. It is possible to achieve both operation and high-capacity cooling in the high-load cooling mode.

  When the illuminance detected by the illuminance sensor is equal to or less than a preset specified value, the control means sets the electric element in an energy saving mode that is an energy saving operation in which the electric element is operated at a rotational speed lower than the rotational speed of the commercial power source. The piston reciprocates in the compression chamber to such an extent that the electric element can be operated at a lower rotational speed than the rotational speed of the commercial power source even during normal cooling when the outside air temperature is around 25 ° C. and the door is not opened and closed. As a result, the cylinder volume, which is a space where the compression operation is performed, was increased. Thus, in order to achieve both the energy saving mode and the high load mode, the cylinder volume considered as an important point of attention by the present inventors needs to be designed in detail so as to be an optimum cylinder volume as a refrigerator. is there.

  When the outside air temperature is around 25 ° C. and the door is not opened and closed, the normal cooling is a range of 25 ° C. ± 2 ° C. when measuring in a closed space such as a constant temperature room as a measurement condition of the refrigerator. It refers to the state where the ambient temperature that is the ambient temperature of the refrigerator is maintained.

  Next, the concept of the cylinder volume of the compressor mounted on the refrigerator will be described.

  To describe from the conclusion, there is an inverter driven hermetic compressor whose cylinder volume of the compressor mounted on the inverter refrigerator is 11.5 to 12.5 cc for R600a and 7 to 7.9 cc for R134a refrigerant. Optimum cylinder volume.

  This is because the loss of the compressor is mainly determined by the motor efficiency, the mechanical efficiency represented by the sliding loss, and the compression efficiency, and varies greatly depending on the cylinder volume and operating conditions. For example, as shown in FIG. 5B, when the cylinder volume is increased and the engine is operated under the same refrigerating capacity, the rotational speed is increased by shifting from A to B and C as the cylinder volume increases, for example, from 10 cc to 12 cc and 15 cc. A significant reduction can be achieved. As a result, the sliding loss also shifts from A to B and C as shown in FIG. 5C. At this time, the sliding loss decreases from one end A to B as the rotational speed decreases. When shifting to C, on the contrary, it increases with an increase in cylinder volume, so that the sliding area increases and the sliding loss tends to increase. Accordingly, it can be understood that, even if only the sliding loss is taken as an example, if the cylinder volume is increased too much, the influence of the sliding loss is superior, so that it is not necessary to increase the overall cylinder volume.

  This is because the compressor is mainly governed by the motor efficiency and mechanical loss influenced by the sliding part and the volumetric efficiency of the compression / suction characteristics. Each loss characteristic is a characteristic as shown in FIG. 11B. Can be represented. Further, FIG. 11C shows the result of summarizing the rotation speed and the refrigerating capacity for each cylinder volume. FIG. 11D shows the relationship between the refrigerating capacity and the COP summarized for each cylinder volume.

  As shown in FIG. 11C, if the cylinder volume is increased, the rotational speed can be greatly reduced. Therefore, the motor efficiency and sliding loss shown in FIG. 11B are compared with A and B in FIG. Loss due to increased cylinder volume is reduced. However, it can be seen that if the cylinder volume is increased too much, the effect of sliding loss is prevailed, so it is not always necessary to increase the cylinder volume.

  On the other hand, it has been clarified in recent years that the storage room has the most influence on power consumption in refrigerators with 550L to 600L under the actual operating condition of the refrigerator. By improving the efficiency of the area B as shown in FIG. It can be seen that the effect of reducing power consumption is maximized.

  From the above, our invention has a good point of about 11.5 to 12.5 cc for R600a and 7 to 7.9 cc for R134a when the relationship between each loss and efficiency is summarized focusing on this use area. I found.

One of the most important issues in increasing the capacity of the refrigerator storage room is the downsizing of the compressor. That is, it is desirable that the outer shell is small and the cylinder volume is large.

  For example, in a cooling system using an R600a refrigerant, a compressor with a large cylinder capacity of about 12 cc and a large piston diameter and stroke (stroke) increase the size of the compressor itself. When mounted on a refrigerator, it was difficult to mount because the volumetric efficiency of the refrigerator deteriorated. However, the outer shell dimensions of the compressor mounted on the refrigerator were the width W (mm), the depth D (mm), When the product of the height H (mm) is the outer shell volume V (mm ^ 3), and the cylinder volume determined by the product of the piston cross-sectional area and the stroke of the compression element of the compressor is K (mm ^ 3), In an ultra-small compressor with V / K of 380 or less or H / K of 0.012 or less, for example, the outer shell size of the refrigerator is 900 mm wide, 730 mm deep, despite the 550 L or higher class, which has been difficult in the past. Height 1800m Allow slim mounted on the refrigerator etc. and then attained the realization of good refrigerator of the volumetric efficiency (the actual contents of the amount of L / outer shell dimensions volume).

  From another viewpoint, the weight of the compressor with respect to the cylinder volume is also important. This is because, for example, in a top unit type compressor having a compressor on the upper side of the refrigerator main body as in the present embodiment, if the weight of the compressor is heavy, the possibility of overturning occurs, Reinforcement design to increase the strength of the refrigerator body is required, and it is desirable to install a lighter weight compressor from the viewpoint of safety and resource saving. For example, when the weight of the compressor mounted on the refrigerator of the present embodiment is G and the cylinder volume determined by the product of the piston cross-sectional area and the stroke of the compression element of the compressor is K, G / K is 0. The super lightweight hermetic compressor below .0006 can dramatically reduce the weight even in a 550 L class refrigerator, and the effect of reducing material costs and transportation costs can be obtained.

  Further, in the compressor with such a high cylinder volume or weight reduction, it is an essential task to prevent temperature, that is, to suppress the temperature rise of the compressor.

  In particular, the higher the cylinder volume, the higher the temperature of the discharged gas, and there is a possibility that the oil deteriorates or the oil film on the valve seating part disappears and chipping occurs.

  In the present embodiment, the temperature rise of the compressor is suppressed by suppressing the increase in the motor temperature by devising the winding ratio of the stator of the motor of the electric element as a countermeasure against this temperature.

  In a reciprocating compressor of 10 cc or more, an inverter driving circuit that drives the electric element at an operating frequency that includes a power element portion and includes a rotational speed that is less than a commercial power supply frequency, and the electric element includes a rotor in which a permanent magnet is embedded; The length of each of the U-phase, V-phase, and W-phase of the winding wound around the teeth portion of the concentrated winding type stator in which the winding is concentrated around the teeth portion provided in the core is L (m). When the wire diameter is D (mm), L / D is 250 or less.

  As described above, when the ratio L / D between the wire diameter and the length is 250 or less, sludge generation due to oil deterioration due to an increase in discharge gas temperature at 10 cc or more due to reduction of Joule heat loss and coating of the valve seating portion The possibility of a defect such as a chipping due to a defect can be suppressed, and a highly reliable compressor can be provided.

  In addition, the compressor of the present embodiment increases the cylinder volume, and is compatible with both the energy saving mode, which is a power saving operation, and the high load mode in which the energy saving mode is canceled and quick cooling is performed. When entering the load mode, there is a concern about an increase in noise.

As one of such noise countermeasures, it is also effective noise reduction means to include a piezoelectric element such as a piezoelectric element in the compressor. This is equipped with a control mechanism that applies a voltage to the piezoelectric element fixed to the sealed container of the compression element and vibrates it. By applying the voltage of the piezoelectric element, it expands and contracts to generate micro vibrations in the sealed container. As a result, it is possible to generate a vibration having a phase opposite to the frequency of the sound whose frequency is desired to be eliminated, so that the vibration from the sealed container can be suppressed.

  Thereby, since the radiated sound and vibration which generate | occur | produced from the airtight container can be suppressed, it can reduce noise and vibration.

  Furthermore, when a conversion mechanism that converts the distortion of a piezoelectric element such as a piezo element fixed to a hermetic casing of a compression element into electric power is provided, the piezoelectric element such as a piezo element is charged when subjected to vibration or distortion. Using the characteristics, the piezoelectric element attached to the hermetic casing can be converted into electric power when subjected to vibration during operation of the compressor. That is, since vibration energy can be converted into other energy, vibration from the sealed casing can be suppressed, so that sound and vibration can be reduced.

  Further, as another form of strain conversion of a piezoelectric element such as a piezo element, a conversion mechanism that converts strain of the piezoelectric element such as a piezo element fixed to a sealed casing of a compression element into electric power may be provided. According to this, by using the converted electric power for the display panel of the refrigerator and the electric power for control, further energy saving can be achieved and further power saving can be realized.

  As described above, when a piezoelectric element such as a piezoelectric element is attached to a sealed container, the shell portion having the largest vibration energy, particularly the upper end portion of the upper container, has a large amount of variation and vibrates the piezoelectric element more actively. It becomes possible to have more energy savings.

  Furthermore, when the piezo element is formed in a fibrous form, not only is the fibrous Peltier device attached to the sealed casing, but it is also included in the steel plate, or a resin material for a compressor such as a protector cover, a resin material for a refrigerator, etc. By containing it, it is possible to save energy by using a supply means that absorbs vibration and converts it into electric energy and supplies the energy to other power supply.

  Further, in the present embodiment, by predicting the usage pattern at home, the door opening / closing is small, food input is small, absence, going out, sleeping, etc. are predicted. Can be suppressed or stopped, energy saving can be realized without taking time and effort to the user, and since it can be visually recognized by the customer by means of notification means such as LEDs, it is possible to appeal energy saving.

  In the present embodiment, the detection means is an illuminance sensor, and prediction is made based on the illuminance change that detects the lifestyle pattern of the consumer. If the detected illuminance value is very small, for example, 5 Lx or less continues for a certain period of time or more, After that, it is predicted that the refrigerator will be used very infrequently, so the illuminance will continue to be low due to suppression of the compressor rotation speed increase and change of the internal temperature setting, and the next door opening and closing Energy saving can be achieved by performing power-saving operation until is performed.

  Also, in this embodiment, by detecting the change in the amount of infrared energy emitted from humans by using a human sensor as the detection means, it can be seen that people around the refrigerator move, If it can be determined that it has not been in the vicinity of the refrigerator for a certain period of time, it will save power until the illuminance continues to be low due to suppression of the compressor rotation speed increase or change of the internal temperature setting regardless of whether it is late at night or until the next door is opened and closed. Energy saving can be achieved by driving.

  In the present embodiment, the detection means is an illuminance sensor, but it may be a standard radio wave receiver that accurately records the time. In this case, since the date and time can be automatically and accurately grasped, the temperature can be adjusted according to the season, and the input to the temperature compensation heater and the like can be reduced at low humidity such as in winter, thereby further saving energy.

  In the present embodiment, the sensor for detecting the surrounding environment of the refrigerator is switched to the power saving operation by the illuminance detected by the illuminance sensor, for example, but the surrounding environment of the refrigerator as represented by the illuminance sensor is detected, for example. The sensor may function not as an absolute condition when starting a power saving operation but as a condition setting means for starting a power saving operation for determining a condition for starting the power saving operation.

  In this case, for example, in the operation state in the main control flow, the illuminance around the refrigerator installation environment is detected by the illuminance sensor, and if the illuminance is 5 lux or less which is the midnight determination value or less, it is determined as midnight, If the number of times the door is opened and closed is not once in the specified time of 5 minutes, the system immediately shifts to low-speed operation at a lower speed than the current speed, while the illuminance around the refrigerator installation environment is at midnight. If this is the case, in order to judge more carefully, power-saving operation is performed by detecting the condition around the refrigerator by setting the strict conditions such as determining the door opening and closing for 3 hours and then proceeding to the next step. It is made to function like changing the weighting of the condition to perform.

  According to this, when it is detected that the person is not active in the environment around the refrigerator, the condition setting for starting the energy saving mode is loosened so that the energy saving mode can be shifted to the energy saving mode more quickly. When it is detected that the activity is in progress, the condition setting for starting the energy saving mode is made strict so as to judge carefully.

  As a result, if the detection means determines that the user is not active, it becomes easier to enter the power saving operation, and the detection means determines that the user is active while quickly entering the power saving operation. If this happens, monitor for a longer period of time compared to the case where the user's activity is detected with a door SW or temperature sensor in the cabinet to carefully determine the user's activity. By doing so, control with high energy-saving effect can be performed with high reliability while appropriately responding to the user's activities.

(Embodiment 2)
11 is a front view of the refrigerator according to the second embodiment of the present invention, FIG. 12 is a cross-sectional view of the compressor according to the first embodiment of the present invention, and FIG. 13A is a crank weight of the compressor according to the present embodiment. FIG. 13B is an enlarged view around the crank weight of the compressor in the reference example , FIG. 14A is an assembly view around the elastic member of the compressor of the present embodiment, and FIG. 14B is the embodiment of the present embodiment. 15A is a cross-sectional view of the periphery of the elastic member of the compressor of the embodiment, FIG. 15A is a perspective view seen from the upper surface of the cylinder block of the compressor of the present embodiment, and FIG. 15B is the cylinder block of the compressor of the present embodiment. FIG. 16A is a plan sectional view around the suction tube of the compressor according to the present embodiment, and FIG. 16B is a longitudinal sectional view around the suction tube of the compressor according to the present embodiment. That.

  In the present embodiment, the same components as those in the first embodiment are denoted by the same reference numerals and the description thereof is omitted. However, the technical idea described in the first embodiment is not limited to the present embodiment unless there is a problem. The present invention can be applied, and the first embodiment and the structure of this embodiment can be combined.

The compressor 28 provided in the refrigerator main body 21 accommodates an electric element 110 including a rotor 111 and a stator 112 and a compression element 113 driven by the electric element 110 in a hermetic container 103. 113 is a piston 1 that reciprocates in the compression chamber 134 and the compression chamber 134.
Inverter electric motor which is a reciprocating type provided with 36 and is operated at a plurality of rotational speeds including a rotational speed lower than the rotational speed of a commercial power source.

  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 sealed container 103 and is provided in the refrigerator via a mount (not shown).

  As described above, the hermetic container 103 is provided with the mechanical part 116 including the compression element 113 and the electric element 110 via the spring 171 which is an elastic member. The machine part 116 is provided at the bottom of the lower container 101 and the lower end of the stator 112. It is elastically supported via a support portion 172 that is a support member that supports the portion 116 and a spring 171.

  A support portion 172 and a spring 171 provided at the lower end of the stator 112 are support members that elastically support the mechanical portion 116.

  The spring 171, which is an elastic member, is provided between the holding portion 173 on the sealed container 103 side and the support portion 172 on the mechanical portion 116 side, and a part is press-fitted and fixed to the holding portion 173 on the sealed container 103 side. It is loosely fitted to the support part 172 on the machine part 116 side with a certain gap in the radial direction.

  In the present embodiment, by using a piston 132 having a large radius, the spring 171, the support part 172 on the machine part side, and the holding part 173 on the sealed container 103 side are configured as follows.

  First, since the unbalance amount increases by using the piston 132 having a large radius, the vertical spring that is the vertical direction is used so that the vibration of the mechanical unit 116 is not easily propagated to the closed container 103 side in a steady operation state. About the fitting of 171, it comprised so that the direction of the support part 172 by the side of a machine part might become what is called loose fitting by which the fitting margin at the time of press injection becomes smaller than the holding | maintenance part 173 side. For example, when a tensile force is applied in the vertical direction, the upper support portion 172 side is pulled out with a smaller load.

  On the other hand, because the diameter of the piston 132 is large, the mechanical block 116 largely swings around the lateral direction, which is the vibration direction of the piston 136, by the repulsive force of the piston 132 not at steady state but at the time of starting and stopping. Since the hook contact phenomenon, which is a phenomenon in which 133 collides with the closed container 103, is likely to occur. As a configuration for reducing the hook contact phenomenon, the horizontal gap 171 with respect to the horizontal spring 171 The support portion 172 on the side is smaller than the holding portion 173, and the side surface of the support portion 172 is likely to hit the spring 171 so as to suppress movement in the lateral direction. For example, when a load is applied in the lateral direction, the support portion 172 side is more likely to collide with the spring 171 than the holding portion 173 side in a portion that is not in contact with the spring 171 from the beginning. In the present embodiment, the gap between the lower end 172 a of the support portion 172 and the spring 171 is configured to be smaller than the gap between the upper end portion 173 a of the holding portion 173 and the spring 171.

  As described above, the relationship between the support portion 172 on the machine portion 116 side and the spring 171 is smaller in the vertical direction than the relationship between the holding portion 173 and the spring 171 and is loose, and in the lateral direction, The structure is more difficult to move.

  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.

  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 eccentrically 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.

  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. Is expanded and reduced to compress the refrigerant 104 in the sealed container 103 and discharge it to the refrigeration cycle.

  Further, the refrigerant is sucked into the compressor from the suction tube 178, sucked from the suction port 179 c of the suction muffler 179, and flows into the compression chamber 134.

  At this time, as shown in FIG. 16A, the center line 178a of the suction tube 178 is located closer to the suction port 179c side of the suction muffler 179 than the corner portion 179b of the receiving portion 179a of the suction muffler 179.

  As shown in FIG. 16B, the center line 178a of the suction tube 178 is located substantially at the center of the suction port 179c of the suction muffler 179.

  Further, in the present embodiment, the relationship between the stroke A that is the distance that the piston 136 reciprocates during the compression operation, the length B of the piston 136, and the diameter C of the piston 136 is A ≦ B ≦ C. The diameter of the piston was increased.

  Specifically, the piston 136 has a diameter C of 27.8 mm and a stroke A which is the distance to which the piston 136 reciprocates is 20 mm, thereby forming a 12 cc compression chamber 134 space as a cylinder volume.

  Further, the length 136 of the piston 136 is 21.5 mm, and the diameter C of the piston 136 is formed to be larger.

  The stroke A is twice as long as the eccentric amount of the eccentric portion 132 formed eccentrically with respect to the main shaft portion 131 of the shaft 130, that is, the eccentric amount in the present embodiment is 10 mm.

  Further, the cylinder block 133 is provided with a bore hole 175 that forms the compression chamber 134 by loosely fitting the piston 136. When the piston 136 is formed large as in the present embodiment, the cylinder block 133 is enlarged. In order to improve the rigidity and obtain sufficient strength, a built-up portion 176a which is a convex portion having a curved surface is provided in the vicinity of the bore hole 175 of the cylinder block 133.

Further, the crank weight 170 provided for balancing the unbalanced load accompanying the reciprocation of the piston 136 is provided in the eccentric portion 132 of the shaft 130 in the same manner as the piston 136, and in the vertical direction of the compression element 113, At least a part of the crank weight 170 is positioned on the horizontal line 136a passing through the upper end of the piston and below the horizontal line 136a passing through the upper end of the piston.

  In the present embodiment, the upper end of the piston 136 is positioned on the horizontal line of the extending portion 170a of the crank weight 170 provided on the lower side of the crank weight 170.

  The electric element 110 has the same configuration as that of the first embodiment, and thus detailed description thereof is omitted.

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

  The control means realizes both a power saving operation in which the electric element 110 is operated at a rotation speed lower than the rotation speed of the commercial power supply and a high load cooling operation in which the electric element 110 is operated at a rotation speed higher than the rotation speed of the commercial power supply. By performing the control, the storage room is cooled to a set temperature.

  In this cooling, when the compressor 28 is energized, electricity is supplied to the stator 112 of the electric element 110, 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 is an inverter compressor that is a variable capacity compressor that can be operated at a plurality of preset rotation speeds.

  Specifically, the number of rotations is set in six stages such as 20 rps, 28 rps, 35 rps, 48 rps, 58 rps, and 67 rps. Further, among the plurality of stages, the maximum is greater than the number of rotations of the commercial power supply, and two at the maximum, and more than half is the number of rotations smaller than the number of rotations of the commercial power supply.

  In a refrigerator equipped with this inverter compressor, in the power saving operation as described above, it is possible to operate at a low rotation speed of 1/3 of 60 Hz which is a frequency of a general commercial power source such as a rotation speed of 20 rotations / s. The rotation speed was set to 28 rotations / s, which is a lower rotation speed than 1/2 of the power supply.

  In the normal cooling mode, which is the normal cooling mode, the rotation speed is set to 35 rpm / center and 48 rps at the maximum, which is lower than the rotation speed of commercial power in Japan.

  Further, the rotation speed of commercial power supply in Japan is 50 rotations / s or 60 rotations / s. However, in this embodiment, the rotation speed of a higher commercial power supply is 60 rotations / s, which is the rotation speed of a general commercial power supply. It was.

  The rotation speed of 60 rotations / s or more is used only when a high load is applied due to a rapid temperature rise caused by opening and closing the door.

As described above, in order to realize energy saving, the present invention uses a compressor having a large cylinder volume in the case of operation in an energy saving mode that is a power saving operation after achieving energy saving in an inverter compressor. In addition, power is saved by operating at low speeds, and when high loads occur due to door opening / closing or rise in the internal temperature, operation at high speeds can be shortened by using a compressor with a large cylinder volume. By performing it in time, it becomes possible to cope with a high load, and it is possible to realize a compressor that achieves significant power saving in the actual refrigerator.

  Furthermore, when using a compressor having a large cylinder volume as described above, the present invention focuses on the correlation between the diameter and stroke of the piston that forms the cylinder volume of the compressor. A compressor with high reliability can be realized even when operating at a wide range of speeds by forming a large cylinder volume by increasing the diameter of the piston instead of forming a large cylinder volume by lengthening Therefore, it is possible to achieve both power saving operation in the energy saving mode and high-capacity cooling in the high load cooling mode.

  Further, the sealed container 103 is provided with a mechanical part 116 including a compression element 113 and an electric element 110 via a spring 171 that is an elastic member, and a holding part 173 and a stator provided at the bottom of the lower container 101. A spring 171 elastically supports the support portion 172 provided at the lower end of 112.

  A support portion 172 and a spring 171 provided at the lower end of the stator 112 are support members that elastically support the mechanical portion 116.

  The spring 171 that is an elastic member is configured such that the gap between the side lower end 172a of the support portion 172 and the spring 171 is smaller than the gap between the side upper end 173a of the holding portion 173 and the spring 171. In the vertical direction, the fitting fit is small, so the looser fits. In the horizontal direction, the gap is small and more difficult to move, and this radial (ie, horizontal) gap suppresses per hook. It functions as a buffer means. In this embodiment, the spring 171, the support portion 172, and the holding portion 173 are all fitted by press fitting, but at least the holding portion 173 side may be press fitted, and the support portion side may be loosely fitted with a gap. . In this case as well, the same effect can be obtained if the spring 171 and the support portion 172 are more easily removed in the vertical direction than the spring 171 and the holding portion 173, that is, can be removed with a small load.

  As a result, the unbalance amount is increased by using the piston 136 having a large radius, so that the vibration of the mechanical unit 116 is not easily propagated to the sealed container 103 side in a steady operation state. As for the fitting of the spring 171, the piston 136 having a large diameter is configured by a so-called loose fitting in which the support portion 172 on the machine portion side has a smaller fitting margin than the holding portion 173 side. Even in the case where is used, vibration transmitted to the outside of the compressor through the sealed container 103 can be suppressed.

  Further, since the diameter of the piston 132 is large, the mechanical block 116 largely oscillates mainly in the lateral direction that is the vibration direction of the piston 136 due to the repulsive force of the piston 132 not at steady state but at the time of starting and stopping. However, when a load is applied in the lateral direction, the support portion 172 is more than the holding portion 173 side in the portion that is not in contact with the spring 171 from the beginning. Since the spring 171 has a gap smaller than the holding portion 173 in the radial direction with respect to the support portion 172 so that the side is more likely to collide with the spring 171, the hook accompanying the start and stop of the mechanical portion 116 is provided. The hit phenomenon can be suppressed.

In the present invention, the crank weight 170 provided to balance the eccentric load accompanying the reciprocation of the piston 136 is provided in the eccentric portion 132 of the shaft 130 in the same manner as the piston 136, and In the direction, at least a part of the crank weight 170 is positioned on the horizontal line 136a passing through the upper end of the piston and below the horizontal line 136a passing through the upper end of the piston 136.

  In the present embodiment, the piston 136 is positioned on the horizontal line of the extension portion 170a of the crank weight 170 provided on the lower side of the crank weight 170.

  That is, in order to balance the unbalanced load accompanying the reciprocating motion of the large piston 136, it is necessary to increase the weight by increasing the shape of the crank weight 170, but when the piston 136 is positioned at the bottom dead center during operation. Since the piston 136 is positioned on the horizontal line of the extension portion 170a of the crank weight 170 and the extension portion 170a is disposed on the main shaft portion 131 side, the crank weight 170 is disposed so as to reduce the overall height of the compressor. Interference between the extension 170a and the piston 136 can be avoided.

  Further, even if the extending portion 170a is positioned below the horizontal line 136a passing through the upper end of the piston 136, the extending portion 170a and the piston 136 are similarly disposed while the crank weight 170 is disposed so as to reduce the overall height of the compressor. Interference can be avoided.

  Therefore, although the weight of the crank weight 170 is increased to increase the weight, the crank weight 170 can be disposed so as to reduce the overall height of the compressor.

  As a result, when mounted in a large-capacity refrigerator that increases the internal capacity, it is possible to reduce the unbalance amount by reducing the size and weight of the piston if the stroke is extended normally. Despite being possible, to reduce the piston unbalance, even if the focus is on increasing the piston diameter, the piston should be as low as possible while reducing the overall height of the compression element. It is devised to have a crank weight in the part close to, which further reduces vibration and reduces the unbalance amount due to the reciprocating movement of the piston, thereby suppressing the twisting of the sliding part and improving reliability. It becomes possible to provide a compressor having a high large cylinder capacity.

  Further, when the refrigerant is sucked into the compressor from the suction tube 178 and sucked from the suction port 179c of the suction muffler 179 and flows into the compression chamber 134, the center line 178a of the suction tube 178 is a receiving portion of the suction muffler 179. 179a is positioned closer to the suction port 179c of the suction muffler 179 than the corner portion 179b, and the center line 178a of the suction tube 178 is positioned substantially at the center of the suction port 179c of the suction muffler 179.

  Thereby, since the compression operation is performed around the low rotation speed by using the compressor having a large cylinder volume, the flow rate of the refrigerant sucked into the suction muffler is reduced. The suction force is reduced, and the refrigerant flowing from the suction tube 178 tends to be exchanged by being released into the high-temperature shell and sucked into the compression chamber at a relatively high temperature. A center line 178a of 178 is positioned on the suction port 179c side of the suction muffler 179 with respect to the corner portion 179b of the receiving portion 179a of the suction muffler 179 in the horizontal direction, and is positioned substantially at the center of the suction port 179c of the suction muffler 179 in the vertical direction. As a result, the suction tube is further connected to the suction pipe 179c of the suction muffler 179. Since the relatively low-temperature refrigerant that has flowed in from the housing 178 can be sucked in, the suction efficiency of the compressor can be improved, and the efficiency of the compressor can be improved. Therefore, a more energy-saving refrigerator compressor is provided. It becomes possible.

Further, the cylinder block 133 is provided with a bore hole 175 that forms the compression chamber 134 by loosely fitting the piston 136. When the piston 136 is formed large as in the present embodiment, the cylinder block 133 is enlarged. In order to improve the rigidity and obtain sufficient strength, a built-up portion 176a which is a convex portion having a curved surface is provided in the vicinity of the bore hole 175 of the cylinder block 133.

  Further, by providing the built-up portion 176b on the opposite side across the bearing hole 177a of the bearing 177 into which the built-up portion 176a and the main shaft portion of the shaft 130 are loosely fitted, the load applied to the bearing 177 can be withstood. Thus, the strength of the entire cylinder block 133 is improved.

  Thus, as the simplest means for improving the strength of the entire cylinder block 133, it is conceivable to increase the volume and weight of the entire cylinder block 133. However, in the present invention, it is possible to save resources in consideration of the environment. In order to improve the strength of the cylinder block 133 efficiently, a built-up portion 176a that improves the strength of the compression chamber 134, and a built-up portion 176b on the opposite side across the built-up portion 176a and the bearing 177, Rigidity is improved by a minimum convex shape that can receive the load of the bearing in a balanced manner, and a cylinder block 133 that is more resource-saving and has high rigidity is formed.

(Embodiment 3)
FIG. 17 is a longitudinal sectional view of a hermetic compressor according to the third embodiment of the present invention, and FIG. 18 is a longitudinal sectional view of a main part of the compression portion according to the same embodiment, and FIGS. 19 (a) and 19 (b). , (C), (d) sequentially show the behavior of the piston in the compression stroke, FIGS. 19 (a), (b), (c) are the initial states of the compression stroke, and FIG. 19 (d) is the compression stroke. The latter states are shown respectively.

  The cylinder block 133 has a substantially cylindrical bore hole 175 and a bearing 177 arranged so as to be fixed to each other at a fixed position, and a piston 323 is removably inserted into the bore hole 175. Thus, a compression chamber 134 is formed.

  In the present embodiment, the same configurations as those in the first and second embodiments are denoted by the same reference numerals, and the description thereof is omitted. However, the technical idea described in the first and second embodiments is not limited to the present embodiment unless there is a problem. The present invention can be applied to the embodiment, and the first and second embodiments and the structure of this embodiment can be combined.

  One end of a connecting rod 137 serving as a connecting means is connected to the eccentric portion 132, and the other end is connected to the piston 136 via a piston pin 136a.

  Here, the bore hole 175 provided in the cylinder block 133 so as to form the compression chamber 134 together with the piston 136 and the valve plate 139 has a bottom dead center from the side where the piston 136 is located at the top dead center as shown in FIG. A taper part 134b whose inner diameter increases from D1 to D3 (> D1) toward the side located at the point, and a position corresponding to the end part on the compression chamber 134 side of the piston 136 reaching the top dead center. Only the section of the direction length L1 is formed to have a straight portion 134a whose inner diameter dimension is constant in the axial direction, and the piston 136 is formed to have the same outer diameter dimension D2 over the entire length.

  As shown in FIG. 3, the bore hole 175 of the cylinder block 133 is formed so that the anti-compression chamber 134 side of the piston 136 is exposed in the sealed container 103 in a state where the piston 136 is located at the bottom dead center. .

  Further, a substantially annular oil supply groove 136b is recessed in the compression chamber 134 side of the outer peripheral surface 136a of the piston 136, and at least a part of the oil supply groove 136b is in a state where the piston 136 is located at the bottom dead center. A notch 120 is formed in which a part of the peripheral wall of the bore hole 175 is notched so as to be exposed from the bore hole 175 and communicated with the sealed container 103.

  The rotor 111 of the electric element 110 rotates the shaft 130, and the rotational movement of the eccentric portion 132 is transmitted to the piston 136 via the connecting rod 137, whereby the piston 136 reciprocates in the compression chamber 134. The reciprocating motion of the piston 136 causes the refrigerant gas to be sucked into the compression chamber 134 from a cooling system (not shown), compressed, and then discharged to the cooling system again.

  Since the pressure in the compression chamber 134 does not increase so much until the piston 136 moves from the bottom dead center position shown in FIG. 3 to the top dead center side in the compression stroke for compressing the refrigerant gas, the outer peripheral surface of the piston 136 Even if the gap between 136a and the tapered portion 134b is relatively large, leakage of the refrigerant gas hardly occurs due to the sealing effect by the refrigerating machine oil 105, and the sliding resistance of the piston 136 is also small.

  Further, the pressure in the compression chamber 134 rapidly increases immediately before the piston 136 reaches a position near the top dead center as the pressure of the refrigerant gas in the compression chamber 134 gradually increases and the piston 136 reaches a position near the top dead center. On the side, the gap between the outer peripheral surface 136a of the piston 136 and the tapered portion 134b becomes small, so that the occurrence of refrigerant gas leakage can be reduced. At this time, the straight portion 134a acts to reduce the leakage of the refrigerant gas that has increased to a predetermined discharge pressure as compared with the case where the straight portion 134a is tapered.

  Further, since the connecting rod 137 side of the piston 136 is exposed from the cylinder block 133 in a state where the piston 136 is located at the bottom dead center, the refrigerating machine oil 105 scattered from the upper end of the shaft 130 is added to the piston 136. The outer peripheral surface 136a is sufficiently supplied and held.

  Further, in a state where the piston 136 is located at the bottom dead center, at least a part of the substantially annular oil supply groove 136b provided on the compression chamber 134 side of the outer peripheral surface 136a of the piston 136 is bored through the notch 120. Since it is formed so as to be exposed from the hole 175, the refrigerating machine oil 105 scattered from the upper end of the shaft 130 is sufficiently supplied to the oil supply groove 136b and held.

  As a result, the refrigerating machine oil 105 supplied to the gap between the inner peripheral surface of the compression chamber 134 formed by the bore hole 175 of the cylinder block 133 and the outer peripheral surface 136a of the piston 136 in the compression stroke also increases.

  Further, since the substantially annular oil supply groove 136b moves to a position facing the straight portion 134a of the bore hole 175, the refrigerating machine oil 105 is easily carried to the straight portion 134a having the largest sliding resistance.

  As a result, a large amount of refrigerating machine oil 105 is supplied to the sliding portion between the cylinder block 133 and the piston 136, the refrigerating machine oil 105 is held well, and the piston 136 is close to the top dead center position. The sliding resistance can be reduced, so that high efficiency can be achieved.

  In the hermetic compressor, the bearing 177 forms a cantilever bearing that pivotally supports the end portion on the eccentric portion 132 side of the main shaft portion 131 of the shaft 130, and the shaft 130 is within the clearance between the main shaft portion 131 and the bearing 177. It is known that the tilt, and the direction and the tilt angle, are complicated behaviors that vary depending on operating conditions.

In particular, it is because of the influence of a complicated load such as a pressure load in the compression chamber 134 and an inertial force of the piston 136 and the connecting rod 137.

  Therefore, the schematic diagram showing the inclination of the shaft 130 shown in FIG. 19 is estimated.

  First, the initial stage of the compression process will be described.

  Although it is not clear how the shaft 130 is inclined even in the initial stage of the compression stroke, as described above, the inclination behavior of the shaft 130 is complicated, and it is considered that the piston 136 behaves complicatedly.

  However, in the initial stage of the compression stroke, since the piston 136 is located within the range of the tapered portion 134b in the compression chamber 134 formed of a cylindrical hole, it can be easily inclined with a slight force. Is considered to slide along one of the inner wall surfaces of the tapered portion 134b.

  Here, the case where the piston 136 is inclined in the same manner as the shaft 130 and slides along the upper tapered portion 134b in the compression chamber 134 formed of a cylindrical hole will be described.

  When the upper outer peripheral surface 136d of the piston 136 moves to the compression chamber 134 side while sliding with the upper taper portion 134b in the compression chamber 134 formed of a cylindrical hole portion, as shown in FIG. The tip edge portion 136c of the lower outer circumferential surface 136e of the piston 136 that does not slide with the 134b contacts the tapered portion 134b facing the upper outer circumferential surface 136d.

  At this time, in the experiments by the inventors, as shown in FIG. 19 (c), the inclination direction of the piston 136 is reversed with respect to the axial center of the compression chamber 134 formed of a cylindrical hole, and until then, the tapered portion 134b and It is presumed that the outer peripheral surface (the lower outer peripheral surface 136e in the above) side that was not slid behaves so as to slide with the tapered portion 134b.

  Starting from the fact that the tip edge portion 136c on the lower outer peripheral surface 136e side of the piston 136 not sliding with the tapered portion 134b is in contact with the tapered portion 134b, the shaft 130 is largely inclined toward the anti-compression chamber, and the piston 136 It is considered that the inclination direction of the cylinder is reversed with respect to the axis of the compression chamber 134 formed of a cylindrical hole.

  In any case, if the compression stroke further proceeds and the pressure of the refrigerant gas in the compression chamber 134 increases after the middle stage of the compression stroke, the compression load of the refrigerant gas is applied to the main shaft on one side with respect to the eccentric portion 132 of the shaft 130. Since the shaft 130 is supported only by the portion 131, the shaft 130 is inclined within the clearance between the main shaft portion 131 and the bearing 177, and largely inclined toward the anti-compression chamber 134 while changing the direction.

  At this time, as shown in FIG. 19 (d), the inclination of the piston 136 is corrected so that the axis thereof substantially coincides with the axis of the straight portion 134a in the compression chamber 134 formed of a cylindrical hole. The refrigerant gas that has moved to the compression chamber 134 side and increased to a predetermined discharge pressure is compressed with less leakage than when the straight portion 134a is tapered.

  The above is a description of the case where the piston 136 is inclined substantially in the same manner as the shaft 130 and slides along the upper tapered portion 134b in the compression chamber 134 formed of a cylindrical hole at the initial stage of the compression stroke. Even when the inclination of the shaft 136 and the shaft 130 are different, at least the piston 136 is considered to be inclined along any part of the tapered portion 134b. Similarly, the inclination direction of the piston 136 is reversed and the tapered portion 134b slides until then. It is assumed that the outer peripheral surface 136a side that has not moved behaves so as to slide with the tapered portion 134b.

  The above is a description of the behavior of the piston 136 with a guess, but the technical idea of the present invention related to the behavior of the piston 136 will be described.

  The experiment was conducted by changing the design specifications of the tapered portion 134b while paying attention to the behavior of the piston 136 described in FIG. 19, and the timing associated with the tip edge portion 136c of the piston 136 contacting the tapered portion 134b is the compression stroke. The result is that the initial taper design has less noise than the taper design after the middle stage of the compression stroke.

  As a cause of this, in the middle and later stages of the compression stroke where the pressure in the compression chamber 134 is high and the compression load is large, the speed at which the tilt direction of the shaft 130 is reversed or the speed at which the tilt direction of the piston 136 is reversed is large. It is presumed that the contact and collision when the outer peripheral surface 136a contacts the tapered portion 134b become severe.

  From the above results and inference, the inclination direction of the piston 136 is formed so as to move with respect to the axial center of the compression chamber 134 formed of a cylindrical hole at the initial stage of the compression stroke. This is because the piston 136 and the cylindrical shape at the time of reversal can be reversed when the piston can move and reversal at the initial stage of the compression stroke, rather than reversing the tilt direction of the piston 136 after the middle of the compression stroke. It can be concluded that the contact with the compression chamber 134 formed of the hole can be alleviated, leading to low noise.

  Specifically, at the initial stage of the compression stroke, the outer circumferential surface 136a of the piston 136 is formed so that the inclination direction of the piston 136 has a margin of movement with respect to the axis of the compression chamber 134 formed of a cylindrical hole. Is moved to the compression chamber 134 side along the tapered portion 134b so that the timing at which the outer peripheral surface 136a contacts the non-sliding tapered portion 134b (see FIG. 5B) is the initial stage of the compression stroke. The taper part 134b is formed in the position of the upstream in a compression stroke, and the compression element 113 is provided so that the straight part 134a may be provided in the downstream of a compression stroke.

  In addition, there is a possibility that the tip 136 of the piston 136 does not contact the tapered portion 134b, and the inclination direction of the piston 136 may be reversed. Even in this case, the same effect can be obtained if the movement margin is the initial stage of the compression stroke. It is thought that.

  Therefore, as one design in which the tip edge portion 136c of the piston 136 contacts the tapered portion 134b in the initial stage of the compression stroke, in the present embodiment, the upper end of the piston 136 on the compression chamber 134 side adjacent to the tapered portion 134b. A straight portion 134a that is constant in the direction of the inner diameter dimension is provided at a portion of the compression chamber 134 that includes a cylindrical hole corresponding to the portion.

  As one of the effects provided with the straight portion 134a, as described above, the leakage of the refrigerant gas increased to a predetermined discharge pressure can be reduced as compared with the case where the straight portion 134a is tapered. By providing the portion 134a, the timing at which the tip edge portion 136c of the outer peripheral surface 136a of the piston 136 contacts the tapered portion 134b on which the outer peripheral surface 136a does not slide can be set as the initial stage of the compression stroke.

  As described above, when the piston 136 is located at the bottom dead center, that is, when it is located at the end point of the suction process (= the start point of the compression stroke), at least the outer peripheral surface 136a on the compression chamber 134 side of the piston pin 136a of the piston 136. It is preferable that a part of the compression chamber 134 is located in the tapered portion 134b, and more desirably, when the piston 136 is located at the bottom dead center, that is, the end point of the suction process (= the start point of the compression stroke). ), The tip end surface 136f of the piston 136 is configured to be positioned at the tapered portion 134b in the compression chamber 134.

  As a result, the piston can always have a margin of movement at the beginning of the compression stroke, and the compression operation can be performed more smoothly. Therefore, as described in detail in the first and second embodiments of the present invention, a large cylinder is used. Despite the fact that when the volume is formed, it is possible to reduce the unbalanced amount by reducing the piston size and weight, usually by increasing the stroke. Even if the focus is on enlarging, the piston always has a vertical allowance in the vertical direction at the beginning of the compression stroke, because the piston diameter is large and the piston length is short. It is possible to provide a highly reliable compressor having a large cylinder volume that suppresses disadvantageous sliding portion twisting and the like.

  Furthermore, the relationship between the stroke A, which is the distance that the piston 136 reciprocates during the compression operation described in detail in the first and second embodiments, the length B of the piston 136, and the diameter C of the piston 136 is as follows. Although the piston is easy to move, such as the sliding portion of the piston whose diameter is increased so as to satisfy A ≦ B ≦ C, the taper portion 134b of the present invention is more prominent. In addition, it is possible to provide a compressor with high reliability and low noise by reducing the piston twist by providing a margin for movement.

  Therefore, a large cylinder volume can be formed by increasing the diameter of the piston, and the load accompanying reciprocation can be further reduced by further reducing the length of the piston. A compressor with high reliability can be realized, and both power saving operation in the energy saving mode and high capacity cooling in the high load cooling mode can be achieved.

  As for the axial length of the tapered portion 134b, the straight portion 134a reduces the leakage of the refrigerant gas in the compression chamber 134, and the timing at which the tip surface 136f of the piston 136 contacts the tapered portion 134b is set to the initial stage of the compression stroke. It is necessary to.

  Here, the initial stage of the compression stroke is the initial stroke by the compression operation on the shaft 130 side from the center in the entire stroke from the bottom dead center to the top dead center (the length of the compression chamber 134 in the reciprocating direction). Is defined in the present invention as the initial stage of the compression stroke.

  In this case, at the initial stage of the compression stroke (up to the midpoint of the reciprocating direction in the compression chamber 134), a part of the outer peripheral surface 136a on the compression chamber 134 side is positioned opposite to the tapered portion 134b with respect to the piston pin 136a. More preferably, it is desirable that the front end surface 136f of the piston 136 is positioned in the tapered portion 134b in the compression chamber 134 at this initial stage.

  Specifically, in the present embodiment, the axial length of the tapered portion 134b is desirably 1/3 or more of the length of the compression chamber 134 in the reciprocating direction, and more desirably 1/2 or more. As for the upper limit, in order to reduce the leakage of the refrigerant gas in the compression chamber 134 at the straight portion 134a at the straight portion 134a, at least the front end surface 136f is at a stroke in which the pressure in the latter stage of the compression stroke is high (last ¼). Since it is desirable to be located in the straight part, the taper part length shall be 3/4 or less of the whole process.

  Furthermore, the inclination direction of the piston 136 is reversed with respect to the axial center of the compression chamber 134 formed of a cylindrical hole, and the outer peripheral surface 136a side that has not been slid with the tapered portion 134b until then slides with the tapered portion 134b. The refrigerating machine oil sprayed horizontally from the upper end of the shaft 130 to the entire circumferential direction in the sealed container 103 even if the outer circumferential surface 136a of the piston 136 contacting the tapered portion 134b is short. 105 is sufficiently supplied.

  Therefore, the refrigerating machine oil 105 sufficiently supplied to the outer peripheral surface 136a of the piston 136 can alleviate the contact between the outer peripheral surface 136a of the piston 136 and the taper portion 134b, thereby realizing high efficiency and low noise. it can.

  Further, an oil supply groove 136b is formed in the outer periphery of the piston 136, and the oil supply groove 136b is a part of the peripheral wall of the compression chamber 134 formed of a cylindrical hole so as to communicate with the inside of the sealed container 103 in the vicinity of the bottom dead center of the piston 136. A cutout portion 120 is formed by cutting out the portion.

  Therefore, the refrigerating machine oil 105 horizontally scattered from the upper end of the shaft 130 in the entire circumferential direction in the sealed container 103 is held in the oil supply groove 136b, and the tapered portion 134b and the straight portion 134a in the compression chamber 134 formed of a cylindrical hole portion. Thus, the sealing effect by the refrigerating machine oil 105 can be obtained, the leakage of the refrigerant gas can be reduced, and the refrigerating machine oil 105 sufficiently supplied to the outer peripheral surface 136a of the piston 136 is replaced with the piston 136. The contact between the outer peripheral surface 136a and the tapered portion 134b can be relaxed, and high efficiency and low noise can be realized.

  In the present embodiment, the connecting mechanism is the connecting rod 137, but the same effect as in the present embodiment can be obtained by using a connecting mechanism having a movable part such as a ball joint.

(Embodiment 4)
FIG. 20 is a characteristic diagram according to the fourth embodiment, in which the horizontal axis indicates the power supply frequency substantially the same as the rotational speed at which the hermetic compressor is operated, and the vertical axis indicates the coefficient of performance C.D. O. P (COEFFICENT OF PERFORMANCE) is shown, FIG. 21 is an enlarged view of elements around a piston used in the fourth embodiment of the hermetic compressor, and FIG. 22 is used for the hermetic compressor in the fourth embodiment. 23 is a front view as seen from the direction B in FIG. 22, FIG. 24 is a top view of the piston used in the hermetic compressor according to the fourth embodiment, and FIG. 25 is a front view as seen from the direction C in FIG. FIG. 26 is a top view of a piston used in the hermetic compressor according to the fourth embodiment.

  In the present embodiment, the piston in the compressor described in the first to third embodiments has a different form (a form in which the weight of the upper side and the lower side of the piston 136 is different), The embodiment is implemented in combination with the embodiment, and a detailed description of the configuration other than the piston is omitted.

  The outer peripheral surface 150 of the piston 136 is formed with a recessed portion 163 that falls inward in the radial direction of the piston 136 around the pin hole 142 into which the piston pin 136a is inserted, and the recessed portion 163 has a first recessed portion 154 on the upper side in the vertical direction. A second recessed portion 155 on the lower side in the vertical direction is provided, and the first recessed portion 154 and the second recessed portion 155 have the same volume.

  The recessed portion 163 is formed so as not to communicate with either the front end surface 136f or the skirt end surface 152 of the piston 136, and the contour line indicating the shape when the recessed portion 163 is planarly developed is not at all with the axial center of the piston 136. The shape does not form parallel lines.

  As can be seen from FIG. 21 showing the state where the piston 136 is located at the bottom dead center, when the piston 136 is located near the bottom dead center, a part of the piston 136 on the skirt end surface 152 side is the bore hole 175 of the cylinder block 133. To be exposed to the space in the sealed container 103.

Further, similarly, as can be seen from the state where the piston 136 is located at the bottom dead center, when the piston 136 is located near the bottom dead center, the first recessed portion 154 and the second recessed portion 15 of the recessed portion 163 are provided.
5 is partially exposed from the bore hole 175 of the cylinder block 133 to the space in the sealed container 103.

  Further, regarding the shapes of the first concave portion 154 and the second concave portion 155 of the concave portion 163, the curvature of the portion 157 protruding to the skirt end surface 152 side of the piston 136 is substantially a straight edge on the tip end surface 136 f side of the piston 136. It is formed to be smaller than the curvature of the R-shape 156 connected to the portion 158.

  The piston 136 is divided into a vertical upper side 192 and a vertical lower side 193 with reference to a plane 195 passing through the axis X and perpendicular to the shaft 130.

  On the upper side 192 in the vertical direction, a cutout portion 194 that is recessed from the skirt end surface 152 toward the front end surface 136f is formed symmetrically.

  By providing the extraction part 194 on the upper side 192 in the vertical direction, the weight of the upper side 192 in the vertical direction of the piston 136 is lighter than the weight of the lower side 193 in the vertical direction. The center of gravity is located in the side 193.

  FIG. 20 shows a result of an experiment performed on the piston 136 having different weights on the upper side and the lower side in the vertical direction, in other words, the piston in the case where the center of gravity of the piston 136 is other than the center in the vertical direction.

  As shown in FIG. 20, as a result of measuring the efficiency of the hermetic compressor in the above configuration, the efficiency of the hermetic compressor in the present embodiment is the hermetic compression in which the center of gravity of the conventional piston is centered in the vertical direction. The result shows that the efficiency of the machine is improved regardless of the number of revolutions operated.

  This improvement in efficiency is directly linked to the suppression of the sliding portion of the compressor and contributes to noise reduction by suppressing the sliding portion of the compressor. The reason for this efficiency improvement will be inferred below.

  When the piston 136 reciprocates in the compression chamber 134, the position of the center of gravity shifts downward in the vertical direction, so that the inertial forces acting on the vertical upper side 192 and the vertical lower side 193 of the piston 136 differ, respectively, and unbalanced. Therefore, the skirt end surface 152 side of the piston 136 is positioned vertically downward in the bore hole 175, and the tip end surface 136f side is positioned vertically upward. Conversely, the skirt end surface 152 side of the piston 136 is vertically aligned in the bore hole 175. It slides while tilting and reversing vertically in the vertical direction, such as being positioned above and the tip surface 136f side being vertically downward, in other words, the piston slides because it has a margin of movement in the vertical direction. I guess it ’s easier.

  The piston 136 inclines and slides to facilitate lubrication by the refrigerating machine oil 105, and in sliding between the piston 136 and the inner wall surface forming the compression chamber 134 of the bore hole 175, the oil film pressure increases, and the piston It is inferred that the sliding loss could be reduced because a stable lubrication state can be formed when the 136 reciprocates.

  Next, the weight of the punched portion 194 will be described.

  As described in the configuration of the piston 194, the weight of the upper side 192 of the piston 136 is formed so as to be lighter than the weight of the lower side 193 of the vertical direction, and it has been confirmed that there is an efficiency improvement effect.

  As described above, the weight on the upper and lower sides in the vertical direction of the piston is made different by the extraction portion 194, and the unbalance amount can be adjusted.

  On the other hand, the oil supply means 120 raises the refrigerating machine oil 105 by the centrifugal force generated with the rotation of the shaft 130, and reaches the eccentric part 132 through the oil supply groove (not shown) of the shaft 130. Is sprayed into the sealed container 103.

  The sprayed refrigerating machine oil 105 hits the contact part 134 and drops and adheres to the outer peripheral surface 150 of the piston 136 from above through the notch part 135.

  At this time, in a state where the piston 136 is located at the bottom dead center, a part including the recessed portion 163 of the piston 136 is formed to be exposed from the cylinder block 133. Therefore, the sprayed refrigerating machine oil 105 is notched. A large amount is directly supplied to the recessed portion 163 of the piston 136 from above through the portion 135 and is held.

  Further, the refrigerating machine oil 105 dropped and adhered to the outer peripheral surface 150 of the piston 136 is supplied to the outer peripheral surface 150 of the piston 136 other than the recessed portion 163, the oil supply groove 136b, and the like as the piston 136 reciprocates. Lubricate between the surface 150 and the bore hole 175.

  In particular, when the piston 136 moves from the bottom dead center to the top dead center, the refrigerating machine oil 105 is effectively drawn between the bore hole 175 and the outer peripheral surface 150 of the piston 136 as the piston 136 moves.

  Here, since the shape when the concave portion 163 is planarly developed forms a curved shape such that the sliding width increases in the skirt direction of the piston 136 so as not to form a parallel line with the axis of the piston 136 at all. The refrigerating machine oil 105 that has entered the recessed portion 163 is easily transported and stored near the substantially straight edge 158 on the distal end surface 136f side of the recessed portion 163, and oil is also supplied from the recessed portion 163 to the oil supply groove 136b. Are stored.

  Therefore, a large amount of refrigerating machine oil 105 is supplied to the sliding portion between the bore hole 175 and the piston 136, and the lubricating oil 106 is held in a good state.

  Due to this action, a sufficient oil film is maintained between the bore hole 175 and the outer peripheral surface 150 of the piston 136, so that a very high sealing performance can be obtained, and an improvement in refrigeration capacity by an improvement in volume efficiency can be obtained. .

  Further, the shape when the recessed portion 163 is developed in a plane does not form any parallel line with the axis of the piston 136, in other words, the shape when the recessed portion 163 is developed in a plane is a parallel line with the axis of the piston 136. It is possible to prevent local wear, such as wear in the reciprocating direction, that occurs when a parallel line with the axis of the piston 136 is formed, and this is extremely coupled with increased lubricity. High reliability can be obtained.

  The above-described technology for improving the lubricity of the piston 136 and the efficiency improving technology for positioning the center of gravity of the piston 136 on the upper side or the lower side in the vertical direction with respect to the axial center each contribute to improvement in efficiency. It is concluded that the technology for improving the lubricity of the piston 136 further improves the technology for improving the efficiency by the center of gravity of the piston 136, and the rate of efficiency improvement is significant compared to a standard hermetic compressor based on the conventional technology. Attached.

Further, when operating at a rotational speed of 23 rps or less, the ratio of the fixed loss to the total loss of the hermetic compressor 164 is large, but in such a low rotational speed operation with a high effect of reducing power consumption, sliding loss is reduced. Reduction and vibration reduction can be realized, and the effect becomes particularly remarkable at low speed operation.

  Further, since the density of the refrigerant R600a is smaller than that of the refrigerant R134a conventionally used in refrigerators or the like, in order to obtain the same refrigeration capacity as the hermetic compressor 164 of the refrigerant R134a, when using the refrigerant R600a, The cylinder volume increases and the outer diameter of the piston 136 increases.

  Furthermore, as described in the first to third embodiments, a compressor with high reliability can be realized even when the engine is operated at a wide speed by forming a large cylinder volume by increasing the diameter of the piston. In the case of a compressor that aims to achieve both power saving operation in the energy saving mode and high-capacity cooling in the high load cooling mode, the piston is configured such that the outer diameter of the piston is increased.

  Therefore, the cross-sectional area of the flow path through which the refrigerant leaks into the sealed container 103 through the gap between the bore hole 175 and the piston 136 is increased, and the refrigerant is liable to leak. However, the piston 136 according to the present embodiment improves the lubricity of the sliding portion between the piston 136 and the bore hole 175 by the lubricity improving technology that the vertical movement is caused by the vertical imbalance in the vertical direction. And the sealing of the gap between the bore hole 175 and the piston 136 is improved.

  Therefore, even when the diameter of the piston 136 is increased as in the present invention, the leakage of the refrigerant 160 can be effectively reduced, and a highly efficient compressor can be provided.

  Moreover, in a refrigerator equipped with a refrigeration apparatus equipped with a highly efficient hermetic compressor 164 as described above, a refrigerator with reduced power consumption can be provided.

  In the present embodiment, on the upper side 192 of the piston 136 in the vertical direction, the extraction part 194 that is recessed from the skirt end surface 152 toward the front end surface 136f is formed symmetrically, but this piston 136 is assembled in reverse. Thus, it has been confirmed by experiments that the efficiency is improved even if the punched portion 194 is positioned below the vertical direction.

  In addition, on the upper side 192 of the piston 136 in the vertical direction, a punched portion 194 that is depressed from the skirt end surface 152 toward the front end surface 136f is provided, and the center of gravity of the piston 136 is located in the lower side 193 in the vertical direction with respect to the axis. However, by not providing the extraction part 194 and making the first recessed part 154 have a larger volume than the second recessed part 155, the center of gravity of the piston 136 is lowered vertically 193 with respect to its axis. Even if it is located inside, it can be similarly implemented.

  Further, none of the punched portion 194, the first recessed portion 154, and the second recessed portion 155 are provided, and the volume of the piston 136 on the vertical upper side 192 and the vertical lower side 193 is different depending on other configurations. Even if it forms, it can implement similarly. For example, a configuration in which a partially different metal is used during operation so that it hardly affects the clearance change between the piston 136 and the inner wall surface forming the compression chamber 134 of the bore hole 175 can be considered.

  As described above, in any case, if the piston 136 is formed so that the center of gravity is located on the upper side 192 or the lower side 193 in the vertical direction with respect to the axis, the efficiency during operation is improved. It has been confirmed that there are many detailed configurations for realizing the configuration.

  For example, configurations other than those shown in FIGS. 22 and 23 are shown in FIGS.

  24 and 25, the extraction portion 194 is a hole provided from the skirt end surface 152 of the piston 136 toward the front end surface 136f, and is symmetric with respect to the vertical plane 199 on the vertical upper side 192 and passing through the axis. In the position. Of course, the present invention can be implemented in the same manner even if the punched portion 194 is positioned below the vertical direction.

  In the present embodiment, the compression element 161 is disposed above the electric element 104. However, the compression element 161 may be similarly disposed even if the compression element 161 is disposed below the electric element 104, but from the viewpoint of vibration. Therefore, it is preferable to dispose the compression element 161 above the electric element 104 to suppress vibration transmission from the compression element 161 serving as the excitation source to the sealed container 103 via the spring 196.

  Further, in order to have vertical movement due to vertical unbalance in the vertical direction, as shown in FIG. 26, as another form in which the weights of the upper side and the lower side of the piston 136 are different. A convex protrusion 136g may be provided on the tip surface 136f of the piston 136.

  It should be noted that the piston shape having the vertical movement allowance due to the vertical imbalance in the vertical direction is further combined with the structure in which the bore hole 175 described in the third embodiment is provided with the tapered portion 134b. Needless to say, a synergistic effect using movement in the direction can be obtained.

  With the structure in which the bore hole 175 described in the third embodiment is provided with the tapered portion 134b, the piston can always have a margin of movement at the beginning of the compression stroke, and the compression operation can be performed more smoothly. Despite the fact that when the cylinder volume is formed, it is possible to reduce the unbalance amount by reducing the size and weight of the piston by increasing the stroke, usually, the diameter of the piston Even if the focus is on increasing the size of the piston, the piston always has an allowance for vertical movement in the initial stage of the compression stroke, so the piston diameter is large and the piston length is short. Therefore, it is possible to provide a compressor having a large cylinder volume that suppresses the twisting of the sliding portion, which is disadvantageous, and has low vibration and high reliability.

  Moreover, power consumption can be reduced by setting it as the freezing refrigeration apparatus (not shown) like the household electric refrigerator which mounts the said closed compressor 164. FIG.

  The refrigerator according to the present invention can be implemented and applied to control in which an illuminance detection means is provided in a household or commercial refrigerator and the operation mode is switched to a power saving operation or the like using the result.

DESCRIPTION OF SYMBOLS 21 Refrigerator main body 22 Refrigerating room 22a Refrigerating room door 23 Ice making room 24 Switching room 25 Freezing room 26 Vegetable room 27 Operation part 27a Operation board 28 Compressor 29 Cooling room 30 Cooler 31 Cooling fan 32 Radiant heater 36 Illuminance sensor 37 Operation switch 38 Indicator light 39 Notification means (LED)
40 Human sensor 41 Illuminance sensor cover 42 LED cover 43 Operation unit cover 51 Door SW
52 Outside temperature sensor 53 Inside temperature sensor 54 Control means 55 Storage means 56 Temperature compensation heater 57 Inside lighting

Claims (5)

A heat insulating box, a refrigeration cycle disposed in the heat insulating box and including a compressor, a condenser, a decompressor, and an evaporator in order to form a series of refrigerant flow paths, and operation of the refrigeration cycle are controlled. A compressor provided in a refrigerator having a control means, wherein the compressor houses an electric element composed of a stator and a rotor and a compression element driven by the electric element in a sealed container, The compression element is a reciprocating type having a compression chamber, a piston that reciprocates in the compression chamber, a shaft having a main shaft portion and an eccentric portion, and a crank weight provided in the shaft. The element includes an electric motor of an inverter that is operated at a plurality of rotation speeds including a rotation speed lower than the rotation speed of a commercial power source, and when a cylinder volume that performs a compression operation is formed by reciprocating a piston in the compression chamber. In addition, It said piston during contraction operation to increase the diameter of the piston than the stroke is the distance the reciprocating,
The crank weight is provided on the upper side of the piston and disposed on a horizontal line passing through the upper end of the piston, and has an extension part on the lower side of the crank weight, and the extension part is provided on the piston. A compressor for a refrigerator, which extends downward from a horizontal line passing through the upper end . The diameter of the piston is increased so that the relationship between the stroke A, which is the distance that the piston reciprocates during the compression operation, the length B of the piston, and the diameter C of the piston satisfies A ≦ B ≦ C. Item 10. A refrigerator compressor according to Item 1. The compression for a refrigerator according to claim 1 or 2, wherein a direction in which the piston reciprocates during the compression operation is a horizontal direction, and a diameter of the piston is 19% or more and 38% or less with respect to a total height of the compressor. Machine. A mechanical part comprising a compression element and an electric element is provided in the sealed container via a spring which is an elastic member, a holding part provided at the bottom of the sealed container, and a support part for supporting the mechanical part 2. The structure according to claim 1, wherein the spring and the supporting portion are more easily supported in the vertical direction than the spring and the holding portion, that is, are removed with a small load. Compressor for refrigerator. A mechanical part comprising a compression element and an electric element is provided in the sealed container via a spring which is an elastic member, a holding part provided at the bottom of the sealed container, and a support part for supporting the mechanical part When the spring is elastically supported by the spring and a load is applied in the lateral direction, the support portion side collides with the spring rather than the holding portion side in a portion that is not in contact with the spring in a steady state. The compressor for a refrigerator according to claim 1, wherein the spring is provided with a gap smaller than the holding portion in the radial direction with respect to the support portion.