JP2016169605A - Compressor and refrigeration apparatus using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor which prevents an increase in lubricant adhesive force between a discharge lead and a spring lead, and has high efficiency.SOLUTION: A compressor is equipped with a compression chamber 118, and a discharge valve device 126. A discharge lead 133 provided on the discharge valve device 126 is provided with an opening portion 133c between an opening/closing portion 133a and a fixed portion 133b thereof, and a spring lead 135 and a stopper 137 are provided with opening portions 135a and 137c in a range including a lead valve seat portion 131. Therefore, contacting areas between the discharge lead 133 and a valve plate 124, and between the discharge lead 133 and the spring lead 135 are reduced, so that lubricant adhesive force is reduced, and the opening delay and closing delay of the discharge lead 133 can be prevented. Consequently, the compressor with high efficiency can be provided.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a compressor and a refrigeration apparatus such as an electric refrigerator, an air conditioner, and a showcase using the compressor.

  In recent years, in order to protect the global environment, the demand for energy saving has been increasing, and even in compressors used in refrigerators and other refrigeration cycle devices, and in air compressors used in industrial fields, etc. There is a strong demand for efficiency.

  Conventionally, this type of compressor has a discharge hole of a discharge valve and a stopper that regulates the lift amount of the discharge lead. Some have achieved low noise (see, for example, Patent Document 1).

  6 (a) and 6 (b) are cross-sectional views of the main part when the discharge lead of the conventional compressor discharge valve device disclosed in Patent Document 1 is opened and closed, and (a) is a cross-section when the discharge lead is closed. FIG. 4B is a cross-sectional view when the discharge lead is opened.

  FIG. 7 is a schematic diagram of the contact range between the discharge lead and the valve plate and the stopper of the conventional compressor. FIG. 7A is a schematic diagram of the contact range between the discharge lead and the valve plate in FIG. (B) is a schematic diagram of the contact range of the discharge lead and the stopper in (b) of FIG.

  6 and 7, a valve plate 24 is attached to the open end of the compression chamber 18. The valve plate 24 includes a discharge hole 30 for discharging the compressed gas compressed in the compression chamber 18, and a reed valve seat portion 31 formed at the peripheral edge of the discharge hole 30 on the side opposite to the compression chamber 18.

  A discharge lead 33 for opening and closing the discharge hole 30 and a stopper 37 for regulating the lift amount of the discharge lead 33 are installed on the side of the valve plate 24 opposite to the compression chamber 18. 31 is arranged to be openable and closable, and the other end together with a stopper 37 is fixedly installed with a fixing portion 33b with a bolt 36 to constitute a discharge valve device 26.

  Further, the discharge lead 33 is provided with an opening 33c serving as a discharge gas passage between the opening / closing portion 33a and the fixing portion 33b.

  The stopper 37 is also provided with an opening 37 c serving as a discharge gas passage at a position substantially coincident with the position of the opening 33 c of the discharge lead 33.

    The operation of the compressor discharge valve device 26 configured as described above will be described below.

  In the intake stroke, as shown in FIG. 6A, the opening / closing portion 33 a of the discharge lead 33 closes the lead valve seat portion 31 to prevent the refrigerant gas from flowing into the compression chamber 18.

    In the discharge process, as shown in FIG. 6B, the pressure of the compressed gas rises and the pressure is applied to the opening / closing part 33a through the discharge hole 30, so that the opening / closing part 33a is pushed up and the compressed gas is discharged. The

    At this time, while the discharge lead 33 is open, the compressed gas is discharged from the gap between the lead valve seat portion 31 and the opening / closing portion 33 a or the gap between the valve plate 24 and the stopper 37.

    In addition, since compressed gas flows also from the openings 33c and 37c of the discharge lead 33 and the stopper 37, overcompression is reduced and efficiency is improved.

Japanese Utility Model Publication No. 63-108573

  However, in the conventional configuration, the behavior of the discharge lead 33 in the discharge stroke is such that the pressure in the compression chamber 18 is a load due to the pressure on the anti-compression chamber 18 side, the spring load of the discharge lead 33, and the inertial force of the opening / closing portion 33a. Then, when the resultant force of the lubricating oil adhesive force on the seal surface between the reed valve seat portion 31 and the opening / closing portion 33a is exceeded, opening begins. Further, the discharge lead 33 reaches the maximum opening amount in the vicinity of the top dead center of the piston 22, and then, the resultant force of the spring load of the discharge lead 33 and the inertial force of the opening / closing portion 33 a is the load due to the above-described differential pressure and the discharge lead 33. When the resultant force of the lubricating oil adhesive force of the contact surface 39b of the stopper 37 is exceeded, the stopper 37 starts to close.

  At this time, the lubricating oil adhesive force of the discharge lead 33 is proportional to the areas of the contact surfaces 39b-1 and 39b-2 shown in FIGS. 7A and 7B, so that the larger the contact area, the more the lubricating oil Adhesive strength is great.

  Further, since the opening amount of the discharge lead 33 changes depending on the operating conditions, the area of the contact surface 39b between the discharge lead 33 and the stopper 37 changes, and the lubricating oil adhesive force also changes.

  Therefore, the opening amount of the discharge lead 33 is increased under the condition that the refrigerant circulation amount is large, such as during high speed operation and low compression ratio conditions, and the area of the contact surface 39b between the discharge lead 33 and the stopper 37 is increased. Since the lubricating oil adhesive force increases, the behavior of the discharge lead 33 is affected, causing a delay in closing, and there is a problem that the performance may deteriorate due to the backflow of the discharge gas to the compression chamber 18.

  The present invention solves the above-described conventional problems, and an object thereof is to provide a highly efficient compressor that prevents a delay in closing a discharge lead even during high-speed operation or a low compression ratio condition and suppresses performance degradation. And

  In order to solve the above-described conventional problems, in the compressor of the present invention, the discharge lead has an opening in a part on the fixed portion side, and the stopper is in a range including the position of the lead valve seat on the central axis. It has an opening.

  As a result, the contact area between the discharge lead and the valve plate in the discharge stroke can be reduced to reduce the adhesive force of the lubricating oil, so that the delay in opening the discharge lead can be prevented and the performance can be improved. Since the compressed gas can be passed through the opening of the stopper, the overcompression loss can be reduced.

Furthermore, the closing delay is prevented by reducing the adhesive force of the lubricant by reducing the contact area between the discharge lead and the stopper when the discharge lead is most open, and the efficiency is improved by suppressing the performance deterioration due to the backflow of the discharge gas to the compression chamber. Can do.

  The compressor of the present invention can prevent the delay in opening and closing of the discharge lead by reducing the lubricant adhesive force of the discharge lead, thereby suppressing the performance deterioration and improving the efficiency.

The longitudinal cross-sectional view of the compressor in Embodiment 1 of this invention Exploded perspective view of the discharge valve device in the first embodiment (A) Sectional view when the discharge lead of the discharge valve device in Embodiment 1 is closed, (b) Sectional view when the discharge lead is open Front view of the discharge valve device in the first embodiment Schematic sectional view of the refrigerator in the second embodiment of the present invention. (A) Main part sectional view of the discharge valve device of the conventional compressor when the discharge lead is closed, (b) Main part sectional view when the discharge lead is opened Schematic showing the contact range between the discharge lead of a conventional compressor and the valve plate and stopper

  According to a first aspect of the present invention, lubricating oil is stored in an airtight container, and an electric element and a compression element driven by the electric element are accommodated. The compression element includes a block forming a cylinder, and an inside of the cylinder. A piston that reciprocates, a valve plate that seals an end of the cylinder to form a compression chamber with the piston, and is formed on the anti-compression chamber side of the valve plate, from the compression chamber to the anti-compression chamber A discharge valve device for discharging compressed gas to the side, the discharge valve device having a discharge hole communicating with the compression chamber and a reed valve seat portion formed on the side opposite to the compression chamber of the discharge hole A discharge lead having an opening / closing portion whose one end opens and closes the reed valve seat portion, a fixing portion whose other end is fixed in contact with the valve plate, and at least one end connects the reed valve seat portion and the fixing portion. A stopper which is fixed on an extension line of the central axis of the discharge lead and regulates an opening amount of the discharge lead, and the discharge lead has an opening in a part on the fixed portion side, and The stopper has an opening in a range including the reed valve seat on the central axis.

  As a result, the contact area between the discharge lead and the valve plate can be reduced to reduce the adhesive force of the lubricant, and the delay in opening the discharge lead can be prevented. Since the compressed gas can be passed through the opening, the overcompression loss can be reduced. In addition, the contact area between the discharge lead and the stopper when the discharge lead is most open is reduced, and the reduction in the adhesive force of the lubricant prevents the delay in closing, thereby suppressing performance degradation due to the backflow of the discharge gas into the compression chamber. The efficiency can be improved.

  According to a second invention, in the first invention, a spring lead made of a leaf spring material is further provided between the discharge lead and the stopper, and the spring lead includes a lead valve seat on the central axis. It has an opening.

  As in the first aspect of the invention, this reduces the contact area between the discharge lead and the valve plate in the discharge stroke, thereby reducing the adhesive force of the lubricating oil and improving the performance by preventing the delay in opening the discharge lead. Furthermore, since the compressed gas can be passed through the openings of the discharge lead, the spring lead, and the stopper, the overcompression loss can be reduced. In addition, since the contact area between the discharge lead and spring lead when the discharge lead is most open can be reduced, the delay in closing can be prevented by reducing the adhesive force of the lubricant, and performance degradation due to the backflow of the discharge gas to the compression chamber is suppressed. The efficiency can be improved.

  In the third invention, in particular, the electric element of the compressor of the first or second invention is driven at a plurality of rotation speeds by an inverter circuit.

  As a result, when driving at a higher frequency than the power supply frequency, the opening amount of the discharge valve is increased in the discharge stroke, the area of the contact surface between the discharge lead, the spring lead and the stopper is increased, and the lubricating oil adhesive force is increased. Easy to grow. However, even under these conditions, the delay in closing the discharge lead can be prevented by reducing the lubricant adhesion by reducing the contact area between the discharge lead and stopper or the discharge lead and spring lead. And the efficiency can be improved.

  The fourth invention is a refrigeration apparatus using the compressor according to any one of the first to third inventions.

  Thereby, the power consumption of a refrigerating apparatus can be reduced by using the highly efficient compressor which prevented the opening delay and closing delay of the discharge lead.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a compressor according to Embodiment 1 of the present invention. FIG. 2 is an exploded perspective view of the discharge valve device according to Embodiment 1 of the present invention. 3A and 3B are cross-sectional views of the discharge valve device according to the first embodiment of the present invention. FIG. 3A shows the discharge lead closed, and FIG. 3B shows the discharge lead opened. FIG. 4 is a front view of the discharge valve device according to Embodiment 1 of the present invention.

  In FIGS. 1 to 4, lubricating oil 102 is stored in a sealed container 101 and an electric compression element 105 including an electric element 103 and a compression element 104 disposed above the electric element 103 is accommodated. The sealed container 101 is filled with a hydrocarbon-based R600a refrigerant 106, and a low-viscosity lubricating oil 102 of VG3 to VG10 is sealed at the bottom.

  The electric element 103 includes a rotor 111 and a stator 112, and is driven by an inverter (not shown) at a plurality of operation frequencies including at least an operation frequency equal to or higher than a power supply frequency. The maximum operating frequency for driving the electric element 103 is 80 Hz, and the electric element 103 is driven at an operating frequency of 17 Hz or more.

  The compression element 104 is arranged in a substantially vertical direction and has a main shaft portion 113 that fixes the rotor 111, a shaft 116 that includes an eccentric shaft portion 114, and an oil supply mechanism 115, and a main bearing that supports the main shaft portion 113 of the shaft 116. 117 and a block 120 having a cylinder 119 that forms a compression chamber 118, a piston 122 that reciprocates in the cylinder 119, a connecting means 121 that connects the piston 122 and the eccentric shaft 114, and an end 123 of the compression chamber 118. And a discharge valve device 126 formed on the non-compression chamber side of the valve plate 124.

The discharge valve device 126 includes a valve plate 124 in which a suction hole 128 that communicates with the inside and outside of the compression chamber 118, a discharge hole 130, and a reed valve seat 131 that is annularly formed on the side of the discharge hole 130 opposite to the compression chamber. And a discharge lead 133 having one end having an opening / closing portion 133a for opening and closing the reed valve seat 131 and the other end being fixed by a fixing portion 133b, and one end being a discharge lead 133. A spring lead 135 that is disposed substantially in parallel with a gap and elastically fixes the fixing portion 133b of the discharge lead 133 at the other end, and a discharge lead 133 that connects the lead valve seat portion 131 and the fixing portion 133b at both ends. A stopper 137 that is fixed on an extension line of the central shaft 134 and restricts the opening amount of the discharge lead 133 and the spring lead 135 is configured.

  Further, the discharge lead 133 has an opening 133c between the opening / closing part 133a and the fixing part 133b. Further, the spring lead 135 and the stopper 137 have openings 135c and 137c in a range including the opening / closing part 133a and the opening 133c of the discharge lead 133.

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

  The rotor 111 of the electric element 103 rotates the shaft 116, and the rotational movement of the eccentric shaft portion 114 is transmitted to the piston 122 via the connecting means 121, so that the piston 122 reciprocates the cylinder 119. Thereby, the refrigerant 106 returns from the cooling system (not shown) into the sealed container 101, is sucked and compressed in the compression chamber 118, and is then discharged again to the cooling system via the discharge valve device 126.

  The lubricating oil 102 is pumped upward by an oil supply mechanism 115 formed on the shaft 116, supplied to the sliding surface between the main bearing 117 and the main shaft portion 113, and formed at the end of the eccentric shaft portion 114. The compression element 104 is lubricated by being scattered horizontally from the scattering hole (not shown) in the entire circumferential direction in the sealed container 101 and supplied to the piston 122.

  Next, the operation of the discharge valve device 126 will be described.

  In the suction stroke, the refrigerant 106 is sucked into the compression chamber 118 from the suction hole 128, and the opening / closing portion 133 a of the discharge lead 133 closes the lead valve seat portion 131, so that the discharged refrigerant 106 flows into the compression chamber 118. There is no.

  Next, the compression stroke is started, and in the latter half, the pressure in the compression chamber 118 rises and high pressure is applied to the opening / closing portion 133a of the discharge lead 133 through the discharge hole 130, so that the opening / closing portion 133a and the spring lead 135 are pushed up. Then, the refrigerant 106 is discharged. When the pressure in the compression chamber 118 decreases, the opening / closing portion 133a of the discharge lead 133 closes the reed valve seat portion 131 again.

  At this time, while the discharge lead 133 is open in the discharge stroke, the compressed gas is discharged from the gap 140 between the reed valve seat portion 131 and the opening / closing portion 133a. In addition, the compressed gas also flows from the discharge lead 133, the spring lead 135, and the openings 133c, 135c, and 137c of the stopper 137.

  Therefore, since the discharge resistance when the compressed gas is discharged from the discharge hole 130 is reduced, the overcompression loss can be reduced.

  Further, the behavior of the discharge lead 133 in the compression stroke is such that the pressure in the compression chamber 118 is the pressure on the non-compression chamber side, the spring load of the discharge lead 133, the inertial force of the opening / closing portion 133a, and the seal of the lead valve seat portion 131. It opens when the resultant force of the lubricating oil adhesion of the surface is exceeded. Further, the discharge lead 133 reaches the maximum opening amount in the vicinity of the top dead center of the piston 122, and then, the resultant force of the spring load of the discharge lead 133 and the inertial force of the opening / closing portion 133a is determined by the differential pressure load inside and outside the compression chamber 118 and the discharge pressure. When the resultant force of the lubricating oil adhesive force of the contact surface 139b between the lead 133 and the spring lead 135 is exceeded, the lead 133 starts to close.

In the present embodiment, since the discharge lead 133 has a shape having an opening 133c between the opening / closing part 133a and the fixed part 133b, the area of the contact surface 139a with the valve plate 124 is reduced by the opening 133c. This reduces the lubricant adhesion.

  As a result, the delay in opening the discharge lead 133 can be prevented, and the performance can be improved.

  In addition, when the refrigerant circulation amount is large, such as during high-speed operation or low compression ratio conditions, the opening amount of the discharge lead 133 increases, and the area of the contact surface 139 between the discharge lead 133 and the spring lead 135 increases frequently. Therefore, there is a tendency that the adhesive force of the lubricating oil increases and the discharge lead 133 is closed late.

  However, in this embodiment, since the area of the contact surface 139b between the discharge lead 133 and the spring lead 135 is reduced by having the openings 133c and 135c, the lubricating oil adhesive force is not excessively increased.

  As a result, the backflow of the refrigerant 106 into the compression chamber 118 due to the closing delay of the discharge lead 133 can be prevented, and the efficiency of the compressor can be improved.

  In the present embodiment, the compressor for the refrigeration cycle using the R600a refrigerant is used. However, other types of compressors may be used as long as the compressor uses a discharge valve device to discharge compressed gas during the compression stroke. A compressor using a refrigerant or a compression mechanism may be used.

  Further, in the present embodiment, the components of the discharge valve device 126 are the discharge lead 133, the spring lead 135, and the stopper 137, but the same operation and effect can be obtained even in a configuration in which the spring lead 135 is omitted. .

  In this embodiment, both ends of the stopper 137 are fixed to the valve plate 124. However, even if only one side is fixed, the behavior of the discharge lead 133 is not affected and the same effect can be obtained.

(Embodiment 2)
FIG. 5 shows a schematic cross-sectional view of the refrigerator in the second embodiment of the present invention.

  In FIG. 5, a heat insulating box 180 injects a heat insulating body 186 for foam filling into a space constituted by an inner box 182 obtained by vacuum molding a resin body such as ABS and an outer box 184 using a metal material such as a pre-coated steel plate. Insulating wall is formed. For the heat insulator 186, for example, a hard urethane foam, a phenol foam, a styrene foam, or the like is used. Use of hydrocarbon-based cyclopentane as the foaming material is better from the viewpoint of preventing global warming.

  The heat insulation box 180 is divided into a plurality of heat insulation sections, and has a configuration in which the upper part is a rotary door type and the lower part is a drawer type. From the top, there are a refrigerating room 188, a drawer type switching room 190 and an ice making room 192 arranged side by side, a drawer type vegetable room 194 and a drawer type freezing room 196. Each heat insulation section is provided with a heat insulation door via a gasket. From the top are the refrigerating room rotary door 198, the switching room drawer door 200, the ice making room drawer door 202, the vegetable room drawer door 204, and the freezer compartment drawer door 206.

  Moreover, the outer box 184 of the heat insulation box 180 is provided with the recessed part 208 which dented the top surface back.

In the refrigeration cycle, the compressor 100 elastically supported by the recess 208 and a heat insulating box 180 are provided.
A condenser (not shown) provided on a side surface, a capillary 212 as a decompressor, a dryer (not shown) for removing moisture, and a cooling fan 214 near the back of the vegetable compartment 194 and the freezing compartment 196 An evaporator 216 arranged and provided and a suction pipe 218 are connected in a ring shape.

About the refrigerator comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.
First, the temperature setting and cooling method of each heat insulation section will be described. The refrigerator compartment 188 is normally set at 1 ° C. to 5 ° C. with the temperature not frozen for refrigerated storage as the lower limit.

  Switching room 190 can change temperature setting by a user's setting, and can be made into predetermined temperature setting from a freezer compartment temperature zone to refrigeration and a vegetable compartment temperature zone. In addition, the ice making chamber 192 is an independent ice storage chamber, and includes an automatic ice making device (not shown) to automatically produce and store ice. Although it is a freezing temperature zone for storing ice, it can also be set at a freezing temperature of −18 ° C. to −10 ° C., which is relatively higher than the freezing temperature zone for the purpose of storing ice.

  The vegetable room 194 is often set to 2 ° C. to 7 ° C., which is a temperature setting equal to or slightly higher than that of the refrigerator room 188. It is possible to maintain the freshness of leafy vegetables for a long period of time as the temperature is lowered so as not to freeze.

  The freezer compartment 196 is normally set at −22 to −18 ° C. for frozen storage, but may be set at a low temperature of −30 ° C. or −25 ° C., for example, to improve the frozen storage state.

  Each chamber is partitioned by a heat insulating wall 187 in order to efficiently maintain different temperature settings. However, it is possible to perform foam filling with the heat insulating body 186 as a method for improving the heat insulating performance at a low cost. Compared to the use of a heat insulating member such as polystyrene foam, the heat insulating performance can be increased by about twice, and the storage volume can be increased by thinning the partition.

  Next, the operation of the refrigeration cycle will be described.

  The cooling operation is started and stopped by a signal from a temperature sensor (not shown) and a control board according to the set temperature in the cabinet. The compressor 100 performs a predetermined compression operation according to the instruction of the cooling operation, and the discharged high-temperature and high-pressure refrigerant gas dissipates heat in a condenser (not shown) to be condensed and liquefied, and is depressurized by the capillary 212 to be low-temperature and low-pressure. To the evaporator 216.

  By the operation of the cooling fan 214, heat is exchanged with the air in the cabinet, the refrigerant gas in the evaporator 216 is evaporated, and the low-temperature cold air after the heat exchange is distributed by a damper (not shown) or the like. Cooling is performed.

  The refrigerator according to the second embodiment is mounted with the compressor described in the first embodiment as the compressor 100 of the refrigerator that performs the above operation. Therefore, the compressor 100 prevents the delay in opening and closing by reducing the adhesive force of the lubricating oil by reducing the contact area of the discharge lead 133, thereby suppressing the overcompression loss and the performance deterioration due to the backflow of the discharge gas to the compression chamber 118. Since the efficiency is improved, the refrigerator equipped with the compressor 100 can reduce power consumption.

  As described above, the compressor according to the present invention can improve efficiency by reducing the contact area of the discharge lead, and can improve efficiency, including a refrigerator for home use, a dehumidifier, a showcase, and a vending machine. The refrigeration apparatus using this compressor can be widely deployed as a refrigeration apparatus with reduced power consumption.

DESCRIPTION OF SYMBOLS 100 Compressor 101 Airtight container 102 Lubricating oil 103 Electric element 104 Compression element 118 Compression chamber 119 Cylinder 120 Block 122 Piston 124 Valve plate 126 Discharge valve device 130 Discharge hole 131 Lead valve seat part 133 Discharge lead 133a Opening / closing part 133b Fixing part 133c Opening Part 134 Central axis 135 Spring lead 135c Opening part 137 Stopper 137c Opening part 180 Thermal insulation box

Claims (4)

The lubricating oil is stored in a sealed container, and the electric element and the compression element driven by the electric element are accommodated,
The compression element includes a block that forms a cylinder, a piston that reciprocates within the cylinder, a valve plate that seals an end of the cylinder to form a compression chamber with the piston, and the valve plate A discharge valve device that is formed on the anti-compression chamber side and discharges compressed gas from the compression chamber to the anti-compression chamber side,
The discharge valve device includes a valve plate having a discharge hole communicating with the compression chamber and a reed valve seat portion formed on a side opposite to the compression chamber of the discharge hole, and an opening / closing portion whose one end opens and closes the reed valve seat portion. A discharge lead having a fixed portion whose other end is fixed in contact with the valve plate, and at least one end is fixed on an extension line of a central axis of the discharge lead connecting the lead valve seat portion and the fixed portion. And a stopper for regulating the opening amount of the
The discharge lead has an opening in a part on the fixed portion side, and the stopper has an opening in a range including the lead valve seat on the central axis. The spring lead made of a leaf spring material is further provided between the discharge lead and the stopper, and the spring lead has an opening in a range including the lead valve seat on the central axis. Compressor. The compressor according to claim 1 or 2, wherein the first electric element is driven at a plurality of rotation speeds by an inverter circuit. A refrigeration apparatus using the compressor according to any one of claims 1 to 3.

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