JP2017223199A - Compressor including oil supply mechanism capable of adjusting oil supply amount - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress a lubrication oil supply amount becoming inappropriate due to fluctuation of an output value of a compressor.SOLUTION: A compressor includes a casing, a compression element, a lubrication oil storage part and an oil supply mechanism 80. The casing has a low-pressure space in which a low-pressure fluid is stored and a high-pressure space 62 in which a high-pressure fluid is stored inside. The compression element 50 has a compression chamber 53, and discharges the high-pressure fluid generated by compressing the low-pressure fluid inside the compression chamber to the high-pressure space. The lubrication oil storage part is provided in the high-pressure space in order to store a lubrication oil. The oil supply mechanism supplies the lubrication oil from the high-pressure space to the compression chamber or a thrust surface 54 in the vicinity. The oil supply mechanism has an adjustment member 82 for adjusting resistance which the lubrication oil receives. The adjustment member makes the resistance in a small pressure difference state in which a pressure difference between the high-pressure space and the compression chamber or the thrust surface smaller than the resistance in a large pressure difference state in which the pressure difference is large.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a compressor including an oil supply mechanism capable of adjusting an oil supply amount.

  A compression element is mounted on a scroll compressor of an air conditioner disclosed in Patent Document 1 (Japanese Patent Laid-Open No. 2015-90093). The compression element includes a fixed scroll fixed to the casing of the compressor and a movable scroll movable with respect to the fixed scroll, and these define a compression chamber for compressing the refrigerant. The compression element is installed so as to divide the internal space of the casing into a low pressure space and a high pressure space. The low-pressure space contains low-pressure refrigerant before and during compression, and the high-pressure space contains high-pressure refrigerant after compression.

  The movable scroll is designed to be pressed against the fixed scroll using a pressure difference between the high pressure space and the low pressure space or the compression chamber. The part where the pressing force is applied at this time is called a thrust surface.

  Since it is necessary to achieve both the tightness and smooth sliding of the fixed scroll and the movable scroll, the lubricating oil is supplied to the sliding portions such as the compression chamber and the thrust surface by the oil supply mechanism. This oil supply mechanism also uses the pressure difference between the high pressure space and the compression chamber to advance the lubricating oil to the sliding portion.

  When the compressor compresses the refrigerant with a high output value in the compression operation, the pressure of the high-pressure refrigerant in the high-pressure space becomes larger. Therefore, the amount of lubricating oil supplied to the sliding portion by the oil supply mechanism may be excessive due to a larger pressure difference. Such excessive supply of lubricating oil can adversely affect the operation of the compressor.

  An object of the present invention is to suppress an inappropriate supply amount of lubricating oil to a sliding portion due to a pressure difference between a high pressure space and a compression chamber.

  A compressor according to a first aspect of the present invention includes a casing, a compression element, a lubricating oil reservoir, and an oil supply mechanism. The casing has a low-pressure space in which low-pressure fluid is accommodated and a high-pressure space in which high-pressure fluid is accommodated. The compression element has a compression chamber, and discharges the high pressure fluid generated by compressing the low pressure fluid in the compression chamber to the high pressure space. The lubricating oil reservoir is provided in the high-pressure space to store the lubricating oil. The oil supply mechanism supplies lubricating oil from the high-pressure space to the compression chamber or the vicinity of the compression chamber. The oil supply mechanism has an adjustment member that adjusts the resistance received by the lubricating oil. The adjusting member makes the resistance in the small differential pressure state where the pressure difference between the high pressure space and the compression chamber or the vicinity is small smaller than the resistance in the large differential pressure state where the pressure difference is large.

  According to this configuration, the resistance received by the lubricating oil is changed by the adjusting member in accordance with the pressure difference between the high-pressure space and the compression chamber or the vicinity thereof. Therefore, the supply amount of the lubricating oil to the sliding portion can be adjusted according to the fluctuation of the pressure difference. As a result, when the pressure difference is large, the amount of lubricating oil supplied to the compression element can be suppressed.

  The compressor which concerns on the 2nd viewpoint of this invention is a compressor which concerns on a 1st viewpoint. WHEREIN: An adjustment member increases resistance in steps according to the increase in a pressure difference.

  According to this configuration, the resistance changes stepwise. Therefore, the optimum one is selected from the plurality of resistors.

  The compressor which concerns on the 3rd viewpoint of this invention is a compressor which concerns on a 1st viewpoint. WHEREIN: An adjustment member increases resistance monotonously according to the increase in a pressure difference.

  According to this configuration, the resistance changes continuously. Therefore, the magnitude of the resistance is optimized.

  The compressor which concerns on the 4th viewpoint of this invention is a compressor which concerns on any one of a 1st viewpoint to the 3rd viewpoint, and an oil supply mechanism further has an oil supply path. The adjusting member is a variable throttle member that is provided in the oil supply passage and adjusts the cross-sectional area of the oil supply passage through which the lubricating oil passes. The variable throttle member changes resistance by moving in accordance with the pressure difference.

  According to this configuration, the variable throttle member moves according to the pressure difference. Therefore, the structure of the oil supply mechanism is simple.

  A compressor according to a fifth aspect of the present invention is the compressor according to the fourth aspect, wherein the variable throttle member is a spiral shaft having a spiral groove biased by a spring. The oil supply passage has a cross-sectional area that varies depending on the region.

  According to this configuration, the spiral shaft moves in the oil supply passage having a cross-sectional area that varies depending on the part. Therefore, the resistance changes as the effective length of the spiral groove changes.

  The compressor which concerns on the 6th viewpoint of this invention is a compressor which concerns on a 5th viewpoint. WHEREIN: A spiral groove has the cross-sectional area which changes with the site | parts of a spiral shaft.

  According to this configuration, the cross-sectional area of the spiral groove changes depending on the portion of the spiral shaft. Accordingly, the resistance received by the lubricating oil is greatly changed by changing the effective sectional area of the spiral groove when the adjusting member is shifted. As a result, the resistance received by the lubricating oil can be changed more greatly with respect to the change in the pressure difference between the high-pressure space and the compression chamber.

  A compressor according to a seventh aspect of the present invention is the compressor according to the fourth aspect, wherein the variable throttle member is a valve body having a tapered shape, which is biased by a spring. The oil supply passage has a cross-sectional area that varies depending on the region.

  According to this configuration, the tapered valve body moves in the oil supply passage having a cross-sectional area that varies depending on the part. Accordingly, the resistance changes as the size of the gap between the oil supply passage and the tapered valve body changes. Therefore, the variable aperture member is easy to manufacture because of its simple shape.

  A compressor according to an eighth aspect of the present invention is the heat-sensitive valve body in which the variable throttle member expands and contracts according to the temperature of the lubricating oil in the compressor according to the fourth aspect.

  According to this configuration, the heat-sensitive valve body expands and contracts according to the temperature of the lubricating oil. The resistance changes as the size of the gap between the oil supply passage and the heat-sensitive valve element changes. Therefore, since the oil supply mechanism does not involve mechanical sliding, it is possible to suppress wear of the component parts.

  The compressor which concerns on the 9th viewpoint of this invention is a compressor which concerns on a 4th viewpoint. WHEREIN: A variable throttle member is an electrically operated valve by which an opening degree is controlled according to the signal of a pressure sensor.

  According to this configuration, the opening degree of the motor-operated valve is electrically controlled. The resistance received by the lubricating oil can be electrically changed according to the pressure in the high-pressure space measured by the pressure sensor. Therefore, fine adjustment of the resistance change with respect to the pressure difference is easy.

  A compressor according to a tenth aspect of the present invention is the compressor according to the ninth aspect, wherein the oil supply passage is partially located outside the casing.

  According to this configuration, the oil supply passage is partially located outside the casing. Therefore, it is easy to install a control component such as an electric valve and a control circuit that controls the control component.

  A compressor according to an eleventh aspect of the present invention is the compressor according to any one of the first to tenth aspects, wherein the compression element includes a fixed scroll and a movable scroll. The fixed scroll is fixed to the casing. The movable scroll can move with respect to the fixed scroll. The compression chamber is defined by a fixed scroll and a movable scroll. The movable scroll is disposed on the thrust surface so as to be pressed against the fixed scroll. The oil supply mechanism supplies lubricating oil to the thrust surface.

  According to this configuration, the lubricating oil is supplied to the thrust surface. Therefore, smooth sliding between the fixed scroll and the movable scroll is maintained while suppressing excessive supply of the lubricating oil.

  In the compressor according to the twelfth aspect of the present invention, in the compressor according to any one of the first aspect to the eleventh aspect, the output value of the compressor when the low pressure fluid is compressed is variable. The compressor generates a small differential pressure state at the first output value and a large differential pressure state at the second output value that is larger than the first output value.

  According to this structure, the resistance which lubricating oil receives is changed according to the output value of the compressor at the time of compressing a refrigerant | coolant. Therefore, the supply amount of the lubricating oil to the sliding portion can be adjusted according to the fluctuation of the output value of the compressor. As a result, when the output value of the compressor is large, the amount of lubricating oil supplied to the compression element can be suppressed.

  In the compressor according to the thirteenth aspect of the present invention, in the compressor according to any one of the first to twelfth aspects, the pressure difference is a pressure difference between the high-pressure space and the compression chamber.

  According to this configuration, the resistance received by the lubricating oil and the amount of the lubricating oil supplied to the compression element are optimized according to the pressure difference between the high-pressure space and the compression chamber.

  According to the compressor according to the present invention, fluctuations in the supply amount of the lubricating oil to the sliding portion are suppressed regardless of fluctuations in the output value of the compressor.

It is sectional drawing of the compressor 10 which concerns on one Embodiment of this invention. It is sectional drawing of the oil supply mechanism 80 of the compressor 10 which concerns on one Embodiment of this invention. It is an enlarged view of the oil supply mechanism 80 of the compressor 10 which concerns on one Embodiment of this invention. It is an external view of 82 A of adjustment members used for the oil supply mechanism of the compressor 10 which concerns on the 1st modification A of this invention. It is a schematic diagram of the oil supply mechanism 80B of the compressor 10 which concerns on the 2nd modification B of this invention. It is a schematic diagram of the oil supply mechanism 80C of the compressor 10 which concerns on the 3rd modification C of this invention. It is a schematic diagram of the oil supply mechanism 80D of the compressor 10 which concerns on the 4th modification D of this invention. It is a schematic diagram of the oil supply mechanism 80E of the compressor 10 which concerns on the 5th modification E of this invention. It is a schematic diagram of the oil supply mechanism 80F of the compressor 10 which concerns on the 6th modification F of this invention.

  Hereinafter, embodiments of an air conditioner according to the present invention will be described with reference to the drawings. In addition, the specific structure of the air conditioning apparatus concerning this invention is not restricted to the following embodiment, In the range which does not deviate from the summary of invention, it can change suitably.

(1) Overall Configuration FIG. 1 shows a compressor 10 according to an embodiment of the present invention. The compressor 10 is mounted on a refrigerant circuit of an air conditioner, sucks and compresses a low-pressure gas refrigerant that is a fluid, and discharges a high-pressure gas refrigerant that is a fluid. The compressor 10 includes a casing 11, a motor 20, a crankshaft 30, a compression element 50, a first bearing 41, a second bearing 42, a third bearing 43, a first support member 70, and a second support member 79.

(2) Detailed configuration (2-1) Casing 11
The casing 11 accommodates the components of the compressor 10 and the refrigerant, and has a strength that can withstand the high pressure of the refrigerant. The casing 11 is provided with a suction pipe 15 for sucking low-pressure gas refrigerant and a discharge pipe 16 for discharging high-pressure gas refrigerant. A lubricating oil reservoir 18 for storing lubricating oil is provided at the bottom of the casing 11. The internal space of the casing 11 includes a low pressure space 61 filled with a low pressure gas refrigerant and a high pressure space 62 filled with a high pressure gas refrigerant. The low pressure space 61 and the high pressure space 62 are separated by a separating member 63.

(2-2) Motor 20
The motor 20 receives power supply and generates power for the compression element 50. The motor 20 has a stator 21 and a rotor 22. The stator 21 is fixed directly or indirectly to the casing 11. The rotor 22 can rotate by performing a magnetic interaction with the stator 21.

(2-3) Crankshaft 30
The crankshaft 30 transmits power generated by the motor 20 to drive the compression element 50. The crankshaft 30 is fixed to the rotor 22 and rotates together with the rotor 22. The crankshaft 30 has a main shaft portion 31 and an eccentric portion 32. The main shaft portion 31 has a cylindrical shape centering on the rotation axis of the crankshaft 30. The eccentric portion 32 is eccentric with respect to the rotation axis of the crankshaft 30.

  The crankshaft 30 is provided with a lubricating oil supply mechanism 34. The lubricating oil supply mechanism 34 supplies lubricating oil to each part of the compressor 10. The lubricating oil supply mechanism 34 includes a lubricating oil pumping mechanism 35 and a lubricating oil supply passage 36.

  The lubricating oil pumping mechanism 35 is provided in the lower part of the crankshaft 30. The lubricating oil pumping mechanism 35 is a mechanism for pumping lubricating oil from the lubricating oil reservoir 18. The lubricating oil pumping mechanism 35 uses the rotation of the crankshaft 30 for pumping operation.

  The lubricating oil supply passage 36 is formed inside the crankshaft 30. The lubricating oil pumped up by the lubricating oil pumping mechanism 35 rises through the lubricating oil supply passage 36. Thereafter, the lubricating oil is supplied to the compression element 50, the first bearing 41, the second bearing 42, and the third bearing 43, and lubricates these sliding portions. Finally, the lubricating oil descends along the surface of the crankshaft 30 and other paths and returns to the lubricating oil reservoir 18.

(2-4) Compression element 50
The compression element 50 is a mechanism that compresses the gas refrigerant. The compression element 50 has a fixed scroll 51 and a movable scroll 52. The fixed scroll 51 is fixed to the casing 11. The movable scroll 52 can revolve with respect to the fixed scroll 51.

  A compression chamber 53 is defined by the fixed scroll 51 and the movable scroll 52. As the movable scroll 52 revolves, the volume of the compression chamber 53 varies, and the gas refrigerant is compressed. The high-pressure gas refrigerant that has undergone the compression process is discharged from the compression element 50 to the high-pressure space 62.

  Due to the difference between the pressure of the high-pressure gas refrigerant filling the high-pressure space 62 and the pressure of the low-pressure space 61 or the compression chamber 53, the movable scroll 52 is pressed against the fixed scroll 51 on the thrust surface 54. When the pressure in the high-pressure space 62 is high, the pressing force is strong, and thus the hermeticity of the compression chamber 53 is easily maintained. In this case, it is sufficient for the compression element 50 to be supplied with the amount of lubricating oil necessary to reduce friction.

  On the other hand, when the pressure in the high-pressure space 62 is low, the pressing force is weak, so that the fixed scroll 51 and the movable scroll 52 are easily separated from each other. Therefore, in order to maintain the hermeticity of the compression chamber 53, it is necessary to fill the gap between the fixed scroll 51 and the movable scroll 52 with lubricating oil. In this case, the compression element 50 further requires an extra amount of lubricating oil not only for the purpose of reducing friction but also for ensuring sealing.

(2-5) First bearing 41, first support member 70
The first bearing 41 is a slide bearing that pivotally supports the main shaft portion 31. The first bearing 41 is supported by the first support member 70. The first support member 70 is made of metal and is fixed directly or indirectly to the casing 11. The first support member 70 supports the fixed scroll 51 directly or indirectly.

(2-6) Second bearing 42, second support member 79
The second bearing 42 is also a sliding bearing that pivotally supports the main shaft portion 31. The second bearing 42 is supported by the second support member 79. The second support member 79 is made of metal and is fixed directly or indirectly to the casing 11.

(2-7) Third bearing 43
The third bearing 43 is a slide bearing that pivotally supports the eccentric portion 32. The third bearing 43 is installed on the movable scroll 52. The eccentric scroll 32 rotates eccentrically while sliding with the third bearing 43, so that the movable scroll 52 can make a revolving motion.

(3) Refueling mechanism 80
FIG. 2 is an enlarged cross-sectional view of the compressor 10 and shows the oil supply mechanism 80. The oil supply mechanism 80 supplies lubricating oil to the compression element 50. The oil supply mechanism 80 includes an oil supply path 81 and an adjustment member 82.

(3-1) Refueling passage 81
The oil supply path 81 is a path for moving the lubricating oil pumped up to the upper part of the crankshaft 30 by the lubricating oil supply mechanism 34 to the compression element 50. The oil supply path 81 includes a support member passage 75 provided in the first support member 70 and a fixed scroll passage 55 provided in the fixed scroll 51. The support member passage 75 and the fixed scroll passage 55 communicate with each other.

  FIG. 3 is an enlarged view of the oil supply mechanism 80. The fixed scroll passage 55 further includes a large diameter passage 56, a small diameter passage 57, and a communication passage 58. The large diameter passage 56 has a large diameter and extends in the vertical direction. The small diameter passage 57 has a smaller diameter than the large diameter passage 56 and extends in the vertical direction. The communication passage 58 includes a path extending in a direction intersecting with the small diameter passage 57 and communicates with the compression chamber 53.

(3-2) Adjustment member 82
The adjustment member 82 shown in FIG. 3 is a variable throttle member that determines the magnitude of the resistance acting on the lubricating oil flowing through the oil supply passage 81. The adjustment member 82 is a spiral shaft, that is, a member having a generally elongated cylindrical shape and a spiral groove 83 formed on the surface thereof. The spiral groove 83 has a uniform cross-sectional area over the entire length of the adjustment member 82. The adjustment member 82 is located over both the large diameter passage 56 and the small diameter passage 57. The upper end of the adjustment member 82 is in contact with a spring 85 attached to the small diameter passage 57.

(4) Refueling Operation In FIG. 2, the first support member 70 is disposed in the high pressure space 62. The pressure of the refrigerant in the compression chamber 53 is generally lower than the pressure of the refrigerant in the high pressure space 62. Therefore, when lubricating oil is present in the support member passage 75, the lubricating oil moves to the compression chamber 53 and the thrust surface 54 due to a pressure difference between the high-pressure space 62 and the compression chamber 53 or the thrust surface 54.

  In FIG. 3, the lubricating oil sequentially passes through the large diameter passage 56, the small diameter passage 57, and the communication passage 58 as indicated by arrows. The adjustment member 82 receives an upward force due to the flow or pressure difference of the lubricating oil. As the adjustment member 82 moves upward, the downward restoring force that the adjustment member 82 receives from the spring 85 increases. As a result, the adjustment member 82 moves to a location where these two forces are balanced.

  In the large diameter passage 56, there is a gap between the outer periphery of the adjustment member 82 and the inner surface of the large diameter passage 56. Therefore, the lubricating oil can pass through this gap. On the other hand, the outer periphery of the small diameter passage 57 and the adjustment member 82 and the inner surface of the large diameter passage 56 are close to each other. Therefore, the lubricating oil travels along the spiral groove 83. Since the cross-sectional area of the spiral groove 83 is extremely small, the lubricating oil is subjected to a large resistance when passing through the small diameter passage 57.

  The output value of the compressor 10 is variable. When the output value of the compressor 10 is large, the motor 20 consumes much electric power and rotates the rotor 22 at high speed. As a result, the compression element 50 compresses the refrigerant in the compression chamber 53 with a high power, and the pressure in the high-pressure space 62 increases. At this time, since the pressure difference between the high-pressure space 62 and the compression chamber 53 or the thrust surface 54 is large, the “high differential pressure state” is entered, so that the speed of the lubricating oil flowing through the oil supply passage 81 increases. Since the upward force that the adjusting member 82 receives from the flow or pressure difference of the lubricating oil increases, the position of the adjusting member 82 shifts upward. The ratio of the portion located in the narrow passage 57 in the adjustment member 82 is increased. Since the length of the spiral groove 83 through which the lubricating oil must pass increases, the resistance that the lubricating oil receives by the adjusting member 82 increases. As a result, the amount of lubricating oil supplied to the compression chamber 53 is suppressed.

  On the other hand, when the output value of the compressor 10 is small, the motor 20 consumes less power and rotates the rotor 22 at a low speed. As a result, the compression element 50 compresses the refrigerant in the compression chamber 53 with a low power, and the pressure in the high-pressure space 62 becomes low. At this time, since the pressure difference between the high-pressure space 62 and the compression chamber 53 or the thrust surface 54 is small, the speed of the lubricating oil flowing through the oil supply passage 81 decreases. Since the upward force that the adjusting member 82 receives from the flow or pressure difference of the lubricating oil becomes small, the position of the adjusting member 82 shifts downward. The ratio of the portion located in the narrow passage 57 in the adjustment member 82 is reduced. Since the length of the spiral groove 83 through which the lubricating oil must pass is shortened, the resistance that the lubricating oil receives by the adjusting member 82 is reduced. As a result, the amount of lubricating oil supplied to the compression chamber 53 is not significantly suppressed.

(5) Features (5-1)
The adjustment member 82 reduces the resistance received by the lubricating oil in the “small differential pressure state”. The adjustment member 82 increases the resistance received by the lubricating oil in the “large differential pressure state”.

  According to this configuration, the resistance received by the lubricating oil is changed by the adjusting member 82 in accordance with the pressure difference between the high-pressure space 62 and the compression chamber 53 or the thrust surface 54 in the vicinity thereof. Therefore, the supply amount of the lubricating oil to the sliding portion can be adjusted according to the fluctuation of the pressure difference. As a result, when the pressure difference is large, the amount of lubricating oil supplied to the compression element 50 can be suppressed.

(5-2)
The adjustment member 82 shifts upward in accordance with the increase in the output value of the compressor 10, thereby increasing the length of the spiral groove 83 located in the small diameter passage 57 and monotonously increasing the resistance received by the lubricating oil.
According to this configuration, the resistance changes continuously. Therefore, the magnitude of the resistance is optimized.

(5-3)
The adjustment member 82 moves according to the pressure difference between the high pressure space 62 and the compression chamber 53 or the thrust surface 54 in the vicinity thereof, thereby changing the resistance received by the lubricating oil.

  According to this configuration, the adjustment member 82 moves according to the pressure difference. Therefore, the structure of the oil supply mechanism 80 is simple.

(5-4)
The adjustment member 82 is a spiral shaft having a spiral groove 83 biased by a spring 85. The oil supply passage 81 includes a large-diameter passage 56 and a small-diameter passage 57, that is, has a cross-sectional area that varies depending on a part.
According to this configuration, the adjustment member 82, which is a spiral shaft, moves in the oil supply passage 81 having a cross-sectional area that varies depending on the part. Therefore, the resistance changes as the effective length of the spiral groove 83 changes.

(5-5)
The oil supply mechanism 80 supplies lubricating oil to the thrust surface 54. Therefore, smooth sliding between the fixed scroll 51 and the movable scroll 52 is maintained while suppressing excessive supply of lubricating oil.

(5-6)
The resistance received by the lubricating oil is changed according to the output value of the compressor 10 when the refrigerant is compressed. Therefore, according to the fluctuation | variation of the output value of the compressor 10, the supply amount to the sliding location of lubricating oil can be adjusted. As a result, when the output value of the compressor 10 is large, the amount of lubricating oil supplied to the compression element 50 can be suppressed.

(5-7)
Depending on the pressure difference between the high pressure space 62 and the compression chamber 53, the resistance experienced by the lubricant and the amount of lubricant supplied to the compression element 50 are optimized.

(6) Modification Examples of the present embodiment are shown below. It should be noted that a plurality of modified examples may be appropriately combined within a range that is consistent with each other.

(6-1) First Modification A
FIG. 4 shows an adjustment member 82B used in the oil supply mechanism of the compressor 10 according to the first modification A of the above embodiment. The adjustment member 82 </ b> A is a spiral shaft having a spiral groove 83. 82 A of adjustment members differ from the adjustment member 82 which concerns on the said embodiment in the point that the cross-sectional area of the spiral groove 83 becomes thin, so that it goes to the lower part.

  According to this configuration, the cross-sectional area of the spiral groove 83 varies depending on the portion of the spiral shaft. Accordingly, when the effective sectional area of the spiral groove 83 is changed when the adjusting member 82 is shifted, the resistance received by the lubricating oil is greatly changed. As a result, the resistance received by the lubricating oil can be changed more greatly with respect to the change in the pressure difference between the high-pressure space 62 and the compression chamber 53.

(6-2) Second Modification B
FIG. 5 shows an oil supply mechanism 80B of the compressor 10 according to the second modification B of the embodiment. The adjustment member 82B is different from the adjustment member 82 that is a spiral shaft according to the above-described embodiment in that the adjustment member 82B is a valve body having a tapered shape.

  According to this configuration, the tapered valve body moves in the oil supply passage having a cross-sectional area that varies depending on the part. The resistance changes as the size of the gap between the oil supply passage and the tapered valve body changes. Therefore, the adjustment member 82B has a simple shape and is easy to manufacture.

(6-3) Third Modification C
FIG. 6 shows an oil supply mechanism 80C of the compressor 10 according to the third modification C of the embodiment. The oil supply mechanism 80 </ b> C includes an oil supply passage 81 and an adjustment member 82 </ b> C provided in the fixed scroll passage 55 that is a part of the oil supply passage 81. The adjustment member 82C is a heat-sensitive valve element that expands as the temperature rises. When the output value of the compressor 10 is large and the pressure in the high-pressure space 62 is high, the temperatures of the high-pressure refrigerant and the lubricating oil tend to be high.

  According to this configuration, the heat-sensitive valve body that is the adjustment member 82C expands and contracts according to the temperature of the lubricating oil. The resistance changes as the size of the gap between the oil supply passage 81 and the adjustment member 82C changes. Therefore, since the oil supply mechanism 80C does not involve mechanical sliding, it is possible to suppress wear of components.

(6-4) Fourth Modification D
FIG. 7 shows an oil supply mechanism 80D of the compressor 10 according to the fourth modification D of the embodiment. The oil supply mechanism 80D includes an oil supply path 81, an adjustment member 82D, a pressure sensor 65, and a control unit 69. The oil supply passage 81 includes a fixed scroll passage 55 and a support member passage 75. The adjusting member 82 </ b> D is an electric valve provided in the fixed scroll passage 55 and capable of controlling the opening degree. The pressure sensor 65 is provided in the high-pressure space 62 and measures the pressure of the high-pressure refrigerant. The pressure difference may be approximated by the detected pressure value of the high-pressure refrigerant, or another pressure sensor may be installed in the low-pressure space 61 or the compression chamber 53 to calculate the pressure difference. The control unit 69 is an electric circuit that controls the opening degree of the motor-operated valve that is the adjustment member 82 </ b> D according to the signal from the pressure sensor 65. The control unit 69 may be installed at any location, and may be provided outside the casing 11, for example.

  According to this configuration, the opening degree of the motor-operated valve that is the adjustment member 82D is electrically controlled. The resistance received by the lubricating oil can be electrically changed according to the pressure in the high-pressure space 62 measured by the pressure sensor 65. Therefore, fine adjustment of the resistance change with respect to the pressure difference is easy.

(6-5) Fifth Modification E
FIG. 8 shows an oil supply mechanism 80E of the compressor 10 according to the fifth modification E of the embodiment. The oil supply mechanism 80E is common to the fourth modification in that it includes an oil supply path 81, an adjustment member 82E, a pressure sensor 65, and a control unit 69, but the configuration of the oil supply path 81 is different from the fourth modification.

  The oil supply passage 81 includes an external passage 95 in addition to the fixed scroll passage 55 and the support member passage 75. The external passage 95 is a pipe provided outside the casing 11.

  According to this configuration, the oil supply passage 81 is partially located outside the casing 11. Therefore, it is easy to install a control part such as an electric valve that is the adjustment member 82E and a control unit 69 that controls the control part.

(6-6) Sixth Modification F
FIG. 9 shows an oil supply mechanism 80F of the compressor 10 according to the sixth modification F of the embodiment. The oil supply mechanism 80 </ b> F includes an oil supply path 81 and an adjustment member 82 </ b> F provided in the fixed scroll passage 55 that is a part of the oil supply path 81. The fixed scroll passage 55 is provided with a narrow portion 55a having a small passage area. The adjustment member 82F is a valve body having a diameter that changes in a plurality of stages, that is, at least two stages. The size of the gap between the adjustment member 82F and the narrow portion 55a determines the resistance of the lubricating oil.

  According to this configuration, the resistance changes stepwise. Therefore, the optimum one is selected from the plurality of resistors.

DESCRIPTION OF SYMBOLS 10 Compressor 11 Casing 15 Intake pipe 16 Discharge pipe 20 Motor 21 Stator 22 Rotor 30 Crankshaft 31 Main shaft part 32 Eccentric part 34 Lubricating oil supply mechanism 35 Lubricating oil pumping mechanism ("pump")
36 Lubricating oil supply passage ("passage")
40 Lubricating oil storage part 41 First bearing (main shaft upper part, rolling bearing)
42 Second bearing (eccentric part / slide bearing)
43 Third bearing (below main shaft)
DESCRIPTION OF SYMBOLS 50 Compression element 51 Fixed scroll 52 Movable scroll 53 Compression chamber 54 Thrust surface 55 Fixed scroll passage 56 Large diameter passage 57 Small diameter passage 58 Communication passage 61 Low pressure space 62 High pressure space 63 Isolation member 65 Pressure sensor 70 First support member 75 Support member Passage 79 Second support member 80 Oil supply mechanism 81 Oil supply passage 82, 82A, 82B, 82C, 82D Adjustment member 83 Spiral groove 85 Spring

Japanese Patent Laying-Open No. 2015-90093

Claims (13)

A casing (11) having therein a low-pressure space (61) in which low-pressure fluid is accommodated and a high-pressure space (62) in which high-pressure fluid is accommodated;
A compression element (50) having a compression chamber (53) and discharging the high-pressure fluid generated by compressing the low-pressure fluid in the compression chamber to the high-pressure space;
A lubricating oil reservoir (18) provided in the high-pressure space for storing lubricating oil;
An oil supply mechanism (80) for supplying the lubricating oil from the high-pressure space to the compression chamber or the vicinity (54) of the compression chamber;
A compressor (10) comprising:
The oil supply mechanism has an adjustment member (82; 82A; 82B; 82C; 82D) for adjusting a resistance received by the lubricating oil;
The adjustment member makes the resistance in a small differential pressure state where the pressure difference between the high pressure space and the compression chamber or the vicinity is small smaller than the resistance in a large differential pressure state where the pressure difference is large.
Compressor (10). The adjusting member increases the resistance stepwise in response to an increase in the pressure difference.
The compressor according to claim 1. The adjusting member monotonously increases the resistance according to an increase in the pressure difference.
The compressor according to claim 1. The oil supply mechanism further includes an oil supply path (81),
The adjusting member is a variable restricting member (82; 82A; 82B) that is provided in the oil supply passage and adjusts a cross-sectional area of the oil supply passage through which the lubricating oil passes,
The variable throttle member changes the resistance by moving in accordance with the pressure difference.
The compressor according to any one of claims 1 to 3. The variable throttle member is a spiral shaft (82; 82A) having a spiral groove (83) biased by a spring (85);
The oil supply passage has a cross-sectional area that varies depending on a part,
The compressor according to claim 4. The spiral groove has a cross-sectional area that varies depending on a portion of the spiral shaft (82A).
The compressor according to claim 5. The variable throttle member is a valve body (82B) having a tapered shape, which is biased by a spring (85),
The oil supply passage has a cross-sectional area that varies depending on a part,
The compressor according to claim 4. The variable throttle member is a heat-sensitive valve element (82C) that expands and contracts according to the temperature of the lubricating oil.
The compressor according to claim 4. The variable throttle member is an electric valve (82D) whose opening degree is controlled in accordance with a signal from a pressure sensor (65).
The compressor according to claim 4. The oil supply passage is partially located outside the casing;
The compressor according to claim 9. The compression element is
A fixed scroll (51) fixed to the casing;
A movable scroll (52) movable relative to the fixed scroll;
Have
The compression chamber is defined by the fixed scroll and the movable scroll;
The movable scroll is disposed on the thrust surface (54) so as to be pressed against the fixed scroll,
The oil supply mechanism supplies the lubricating oil to the thrust surface;
The compressor according to any one of claims 1 to 10. The output value of the compressor when compressing the low-pressure fluid is variable,
The compressor produces the small differential pressure state at a first output value and the large differential pressure state at a second output value greater than the first output value;
The compressor according to any one of claims 1 to 11. The pressure difference is a pressure difference between the high-pressure space and the compression chamber.
The compressor according to any one of claims 1 to 12.

Images