JPH0933121A - Compressor for heat pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To conduct smooth lubrication of a pressurizing chamber upon operating a compressor again. SOLUTION: A compressor for heat pump is formed in two wall members and equipped with compressors A, B, having a pressurizing chamber 107, a pressurizing means, pressurizing refrigerant by the relative motion of one of two wall members with respect to the other of the same, a lowpressure side refrigerant passage, guiding the refrigerant from a lowpressure circuit in a refrigerant circuit 6 into the pressurizing chamber 107, and a high-pressure side refrigerant passage, guiding the refrigerant, discharged out of the pressurizing chamber 107, into a high-pressure circuit in the circuit 6. An oil reservoir 119, separating the lubricating oil in the pressurized refrigerant and reserving it, a first oil passage K, communicating with the low-pressure refrigerant passage, and a second oil passage L, having an opening at a position higher than the oil reservoir side opening of the passage K and communicating with the low-pressure refrigerant passage, are arranged whereby the passage L communicates with the low-pressure side refrigerant passage at the upstream part of the passage K.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump compressor that is driven by an engine to circulate the refrigerant in a refrigerant circuit.

[0002]

2. Description of the Related Art A heat pump is used as an air conditioner or a refrigerator, for example, by making an engine for driving a compressor and a compressor circulate a refrigerant in a refrigerant circuit.

In this heat pump, for example, a compressor is arranged in the middle of a refrigerant circuit, is formed inside at least two wall members, and a pressurizing chamber for pressurizing the refrigerant and one of the two wall members are arranged in the other. Pressurizing means that pressurizes the refrigerant by moving relative to it, a low-pressure side refrigerant passage that guides the refrigerant from the low-pressure circuit in the refrigerant circuit to the pressurizing chamber, and the refrigerant discharged from the pressurizing chamber to the refrigerant circuit. And a compressor having a high-pressure side refrigerant passage leading to a high-pressure circuit inside the high-pressure circuit, and at least one of the high-pressure circuit or the high-pressure side refrigerant passage is provided with an oil reservoir for separating and storing lubricating oil in the pressurized refrigerant. However, there is an arrangement in which an oil passage that connects the oil reservoir and the low-pressure side refrigerant passage is arranged.

As a result, the lubricating oil is circulated to the low pressure side refrigerant passage due to the pressure difference between the pressure in the oil reservoir during operation and the pressure in the low pressure side refrigerant passage, and the lubrication between the two wall members is performed thereafter. With the pressurized refrigerant, it entered the high pressure side refrigerant passage, returned to the oil reservoir, and was able to continue lubrication.

[0005]

When the compressor is stopped, since the refrigerant in the low pressure circuit and the low pressure side refrigerant passage is at low temperature and low pressure, it is condensed before the refrigerant in the high pressure circuit and the high pressure side refrigerant passage. However, a pressure difference occurs between the high pressure side refrigerant passage and the low pressure side refrigerant passage even if the operation is stopped.

Therefore, even if the refrigerant does not move in the refrigerant circuit, the lubricating oil in the oil reservoir flows through the oil passage to the low pressure side refrigerant passage. Further, since the refrigerant does not move in the low pressure circuit, the lubricating oil may flow back through the refrigerant circuit.

Therefore, all the lubricating oil in the oil sump flows out from the low pressure side refrigerant passage into the low pressure circuit, and when the compressor is operated again, the lubricating oil in the oil sump cannot be supplied through the oil passage. Moreover, the lubricating oil in the low pressure circuit cannot immediately provide lubrication between the two wall members.

The present invention has been made in view of the above point, and the invention according to claim 1 provides a compressor for a heat pump capable of smoothly lubricating the pressurizing chamber when the operation is performed again. Is intended. Another object of the present invention is to provide a compressor for a heat pump, which can smoothly lubricate not only the pressurizing chamber but also the lubrication portion after re-driving. Further, claim 3
It is an object of the invention described above to provide a compressor for a heat pump that can smoothly perform lubrication when it is operated again. It is an object of the invention according to claim 4 to provide a compressor for a heat pump, which has a simple and compact structure and can smoothly perform lubrication when it is re-operated.

[0009]

In order to solve the above problems and to achieve the object, the invention according to claim 1 is arranged in the middle of a refrigerant circuit of a heat pump and is formed inside at least two wall members. And a pressurizing chamber in which the refrigerant is pressurized,
A pressurizing means for pressurizing the refrigerant by moving one of the two wall members relative to the other; and a low pressure side refrigerant passage for guiding the refrigerant from the low pressure circuit of the refrigerant circuit to the pressurizing chamber. A compressor having a high-pressure side refrigerant passage that guides the refrigerant discharged from the pressurizing chamber to a high-pressure circuit inside the refrigerant circuit, and is pressurized in at least one of the high-pressure circuit or the high-pressure side refrigerant passage. An oil reservoir for separating and storing lubricating oil in the refrigerant is arranged, and the oil reservoir communicates with the low pressure side refrigerant passage in the compressor and the low pressure refrigerant passage including the low pressure circuit. In a lubricating device for a heat pump compressor, the second oil passage having an opening arranged above the oil reservoir side opening of the first oil passage and communicating with the low-pressure refrigerant passage. Is characterized in that the placed.

Therefore, when the operation is stopped, a differential pressure is generated at both ends of both the first oil passage and the second oil passage, and the lubricating oil flows from the oil reservoir to the low-pressure refrigerant passage. However, when the opening of the second oil passage comes out of the oil surface, the refrigerant flows through the high pressure side refrigerant passage and the second oil passage to the low pressure refrigerant passage. This is because the gas refrigerant, which has a lower viscosity than the lubricating oil, is more likely to flow, so that a larger amount than the lubricating oil flow in the first oil passage flows and the differential pressure between both ends of both oil passages is immediately lost. The flow of the lubricating oil in the first oil passage is stopped, and the lubricating oil having an oil level of the height between the opening of the first oil passage and the opening of the second oil passage remains in the oil sump.

Therefore, when the compressor is re-driven, a differential pressure is generated in both oil passages, and the refrigerant passes through the second oil passage. However, since the lubricating oil flows through the first oil passage, the initial pressure is increased. Poor lubrication in the pressure chamber can be eliminated. After that, the lubricating oil that has flowed out to the low-pressure refrigerant passage at the time of operation stop returns to the oil reservoir, and the oil level returns to the upper part from the opening of the second oil passage.

According to a second aspect of the present invention, one of the wall members is made stationary and the other is moved, and the other moving wall member is driven, and a drive device having a lubricating portion is arranged. By disposing the lubricating portion in the middle of the first oil passage, the lubricating oil from the oil sump is guided to the low pressure side refrigerant passage after passing through the lubricating portion.

As a result, since the opening on the oil sump side of the first oil passage is at a low position, when re-driving the compressor, the lubricating oil entering the first oil passage from this opening passes through the lubrication section. Outflowing to the low-pressure refrigerant passage, this lubricating oil further lubricates the pressure chamber.

According to a third aspect of the present invention, a check valve for allowing a flow in the direction of the pressurizing chamber is arranged in the middle of the low pressure side refrigerant passage, and at least a second oil is provided downstream of the check valve. It is characterized by communicating with the passage.

Therefore, when the compressor is stopped, the lubricating oil flowing out to the low-pressure side refrigerant passage through the second oil passage is on the downstream side of the check valve and cannot flow on the upstream side any further. Absent. Therefore, when the compressor is restarted, this lubricating oil quickly lubricates the pressure chamber and returns to the oil reservoir.

According to a fourth aspect of the present invention, the first oil passage and the second oil passage are integrated into one oil passage, and the opening of the oil passage on the oil sump side is two.
The feature is that the positions of the first opening and the second opening are set up and down.

Therefore, even if the operation is stopped, if the lubricating oil flows through the oil passage to lower the oil level and expose the second opening above the oil level, the refrigerant flows from the second opening to the first opening. From this, lubricating oil is introduced into the oil passage and flows into the low-pressure refrigerant passage in a gas-liquid mixed state. And
The pressure difference disappears, and the oil level reaches the middle portion between the first opening and the second opening. After that, when the compressor is driven again,
A differential pressure is generated in the oil passage, and a mixed fluid of oil and a gas-phase refrigerant flows into the low-pressure refrigerant passage to lubricate the pressurizing chamber.

[0018]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of an air conditioner including a compressor for a heat pump according to the present invention will be described below with reference to the drawings.

FIG. 1 is a schematic diagram of an air conditioner equipped with a heat pump compressor. The air conditioner 1 includes an engine unit 2, a compressor system unit 3, a heat pump unit 4
Is provided, a hot water circuit 5 for circulating the cooling water of the engine unit 2 is provided between the engine unit 2 and the heat pump unit 4, and the compressor system unit 3 and the heat pump unit 4 are provided.
A refrigerant circuit 6 that compresses and circulates a refrigerant such as CFC is provided between and. The engine unit 2, the compressor system unit 3, and the heat pump unit 4 are controlled by the control unit 8 based on an instruction from the operation unit 7.

The engine unit 2 is provided with an actuator unit 9 and a sensor unit 10, engine information from the sensor unit 10 is sent to the control unit 8, and the actuator unit 9 is controlled by an instruction from the control unit 8 to control the engine 2 Is driven. A mixture of air and fuel gas is sucked from the intake system of the engine unit 2 and burned, and exhaust gas is discharged from the exhaust system. The compressor system unit 3 is driven by the operation of the engine unit 2.

The compressor system unit 3 is provided with a plurality of compressors, and controls the number of compressors in the compressor system unit 3 in accordance with an air conditioning load based on an instruction from the control unit 8. The heat pump unit 4 is driven via the refrigerant circuit 6 by the operation of the compressor system unit 3.

The heat pump unit 4 includes an actuator unit 1
1 and the sensor unit 12, the heat pump information from the sensor unit 12 is sent to the control unit 8, and the actuator unit 11 is controlled by an instruction from the control unit 8 to perform air conditioning between heating and cooling.

The control unit 8 includes a control unit 13 and a storage unit 1.
4 and drive means 15 are provided, and the control means 13 drives the drive means 15 based on instructions from the operation unit 7 and information stored in the storage unit 14, engine information from the sensor unit 10, and heat pump information from the sensor unit 12. The driving means 15 drives the actuator section 9 of the engine section 2, the compressor system section 3 and the actuator section 11 of the heat pump section 4.

The operation unit 7 includes a switch unit 16 and a display unit 1.
7, the operator operates the switch unit 16 to send an instruction signal to the control unit 8 to operate the air conditioner 1, and the operating state is displayed on the display unit 17.

Next, the detailed structure of the air conditioner 1 having the heat pump compressor will be described in detail with reference to FIGS. 2 and 3. 2 is a schematic configuration diagram of an air conditioner including a heat pump compressor during cooling operation, and FIG. 3 is a schematic configuration diagram of an air conditioner including a heat pump compressor during heating operation.

In the figure, reference numeral 1 is an air conditioner,
The air conditioner 1 includes an outdoor unit 21 and an indoor unit 2
It consists of two. The engine unit 2, the compressor system unit 3, the hot water circuit 5, and the refrigerant circuit 6 are provided in the outdoor unit 21, and the heat pump unit 4 is provided in the outdoor unit 21.
And an indoor unit 22.

The engine section 2 is provided with a water-cooled engine 23, and a mixer 25 and an air cleaner 26 are connected to the water-cooled engine 23 via an intake pipe 24, and the air is supplied from the air cleaner 26 to the mixer 25. In addition, the flow control valve 2 is connected to the mixer 25 via a pipe 27.
8, the governor 29 and the solenoid valve 30 are connected, and the operation of these elements causes fuel gas to flow from a fuel cylinder (not shown) to the mixer 2
5 is supplied. The mixer 25 mixes the fuel gas and air by the operation of the throttle by the pulse motor 31 and supplies the mixed gas to the water-cooled engine 23.

Further, in the water-cooled engine 23, an electromagnetic valve 33 is provided through an oil pipe 32 and an oil tank 3 is provided at an upper position.
4 is connected, the solenoid valve 33 is automatically opened when the amount of oil decreases, and the oil is supplied from the oil tank 34 to the water-cooled engine 23 by gravity. An exhaust heat exchanger 36, an exhaust silencer 37, and a mist separator 38 are connected to the water-cooled engine 23 via an exhaust pipe 35. When the exhaust gas from the water-cooled engine 23 flows through the exhaust heat exchanger 36 and the exhaust silencer 37, it is cooled and separated from the exhaust gas to produce drain water having an acidic content. Also in the mist separator 38, drain water separated from the exhaust gas and having an acidic content is generated. These drain waters are introduced into the drain water treatment device 40 through the pipes 39, and the drain water treatment device 40 neutralizes the drain water and discharges the drain water. The engine section 2 is provided with a heater 41, and the heater 41 adjusts the oil temperature in the oil pan of the water-cooled engine 23.

The compressor system section 3 is provided with two compressors A and B, and these two compressors A and B are connected to an output shaft 44 of the water-cooled engine 23 via an electromagnetic clutch 43, respectively. It Each electromagnetic clutch 4
Reference numeral 3 is a clutch drive member (not shown) that controls connection and disconnection. Reference numeral 45 denotes a heater for adjusting the oil temperature in the compressors A and B, which generates heat when starting at low temperature.

The refrigerant circuit 6 compresses and circulates the refrigerant,
It functions as a heat pump by vaporizing and liquefying. The refrigerant circuit 6 includes a base circuit 47 forming a circuit from the compressors A and B of the compressor system unit 3 to the four-way valve 46, an indoor circuit 48 arranged in the indoor unit 22, a base circuit 47 and an indoor circuit 48. And an outdoor circuit 49 arranged between the and.

The base circuit 47 is connected to the discharge ports of the compressors A and B, and is connected to the first port 46a of the four-way valve 46 and the discharge side circuit 50 and the second port 46b of the four-way valve 46. The suction side circuit 51 communicates with the suction port sides of A and B. An oil separator 52 is installed in the discharge side circuit 50, a heater 53 is provided in the oil separator 52, and the temperature of the oil separator 52 is adjusted by the heater 53. Oil separator 52
Allows the lubricating oil to pass through the strainer 54 and
5 is returned to the downstream side of the sub accumulator 56,
Further, it is returned to the upstream side of the main accumulator 58 via the suction valve 57. After starting, the suction valve 57 is opened when a large amount of lubricating oil flowing out from the compressors A and B collects in the oil separator 52, and is closed in other cases.

The sub accumulator 56 is provided integrally with the compressor system section 3, and the main accumulator 58 is provided in the suction side circuit 51. Liquid and gas of the refrigerant are contained in the main accumulator 58, and the gas flows from the circuit 51c to the capillary tube 60 and the circuit 51.
It is sent to the sub accumulator 56 by d, 51e and 51F, and also by the strainer 61 and the capillary tube 62, and circuits 51d, 51e and 51F. The liquid of the refrigerant in the main accumulator 58 is sent to the sub accumulator 56 by the strainer 63, the capillary tube 64, and the circuits 51d, 51e, 51F. Temperature sensors 59a, 5
9b are for measuring the temperature when the liquid refrigerant passes through the strainer 63 and the capillary tube 64, and the temperature when the liquid refrigerant passes through the strainer 61 and the capillary tube 62, respectively, to detect the height of the liquid surface. . The main accumulator 5
Lubricating oil and liquid refrigerant from the bottom in
g, strainer 77, control valve 78 and orifice 79
To the sub accumulator 56 via the circuits 51e and 51F.

The sub accumulator 56 has a heater 65.
Is provided, and the sub accumulator 5 is provided by the heater 65.
A temperature control of 6 is performed. The refrigerant gas in the sub accumulator 56 is sucked through the circuits 602 and the check valve 601 by driving the compressors A and B, respectively. The lubricating oil and the liquid refrigerant accumulated in the sub accumulator 56 are gradually sucked into the compressors A and B from the orifice 66. Further, the discharge side circuit 50 is connected to the suction side circuit 51 by a strainer 68 and an electromagnetic valve 69 which is opened when the pressure is abnormally high, and prevents an abnormal rise in pressure.

A circuit 49a forming an outdoor circuit 49 is connected to the third port 46c of the four-way valve 46, and an outdoor heat exchanger 70 is installed in this circuit 49a. The outdoor heat exchanger 70 and the indoor heat exchanger 71 of the indoor circuit 48.
A circuit 49b in which a heat exchanger 72 provided in the main accumulator 58, a strainer 73, and a manual valve 74 are arranged, a joint 75, and an electronic expansion valve 76 are connected between and.

An indoor heat exchanger 71 for exchanging heat in the room is connected to the indoor circuit 48. The indoor heat exchanger 71 is a circuit 49c constituting a connecting pipe (joint) 80 and an outdoor circuit 49. Also, the base circuit 47 and the fourth port 46d of the four-way valve 46 arranged in the middle of the outdoor circuit 48 are communicated with each other via a manual valve 81 arranged in the middle thereof.

The suction side circuit 51 is connected to the circuit 49b constituting the outdoor circuit 49 via the control valve 90 and the strainer 91, and the discharge side circuit 50 is further connected to the circuit 49b and the strainer 92, the solenoid valve 93 and the capillary tube 94. Connected through.

The hot water circuit 5 includes a water-cooled engine 23, which serves as a heat source for hot water, and a heat exchanger 82, which includes a cooling water jacket.
The hot water has a switching valve 83 having a thermostat by the action of the pumps 86, 87, a linear three-way valve 84, a radiator (radiator) 85, a pump 86, an exhaust heat exchanger 36,
Circulates via pump 87. At the time of startup, the switching valve 83 having a thermostat is operated to return the hot water to the heat exchanger 82 via the pump 87 and circulate the hot water until the hot water reaches a predetermined temperature. Further, when the ratio of the heat radiation amount to the heat absorption amount in the indoor heat exchanger 71 and the outdoor heat exchanger 70 that function as a condenser or a radiator increases, the three-way valve 84 operates so that the hot water heat exchanger 88 of the main accumulator 58.
The temperature of the main accumulator 58 is adjusted.

Therefore, in the air conditioner 1 thus constructed, as shown in FIG. 2, the four-way valve 46 is operated to operate the first port 46a and the third port 46c when operating as a cooling system. And the fourth port 46d and the second port 46b are simultaneously communicated with each other.

As a result, the water-cooled engine 23 drives the compressors A and B to compress the refrigerant, which is compressed.
The high-temperature, high-pressure refrigerant gas is liquefied by being cooled by the outside air in the outdoor heat exchanger 70 of the outdoor unit 21. The liquefied refrigerant is decompressed by the operation of the electronic expansion valve 76, and the low-pressure refrigerant liquid is used for the indoor heat exchanger 71 of the indoor unit 22.
The heat is taken from the room air to evaporate. The cooling effect is generated by the evaporation heat at this time, and the room is cooled. The evaporated refrigerant gas returns to the compressors A and B again, and the same cycle is repeated. When a heat pump device is used as a refrigerator, the refrigerant is circulated in this manner with the four-way valve 46 abolished. Then, the indoor heat exchanger 7 is installed in a showcase or a freezer.

In the case of operating as heating, as shown in FIG.
As shown in, the four-way valve 46 is operated to operate the first port 4
6a communicates with the fourth port 46d, and the third port
The port 46c of is connected to the second port 46b.

As a result, the water-cooled engine 23 drives the compressors A and B to compress the refrigerant, which is compressed.
The high-temperature, high-pressure refrigerant gas is cooled by the indoor air and liquefied in the indoor heat exchanger 71 of the indoor unit 22.
At this time, the room air is warmed by the heat of condensation to produce a heating effect. The liquefied refrigerant is decompressed by the operation of the electronic expansion valve 71, and the refrigerant liquid having a low pressure deprives the heat of the outside air by the outdoor heat exchanger 70 of the outdoor unit 21 and at the same time the hot water heat exchange from the hot water circuit 5 through the three-way valve 84. The refrigerant gas that has exchanged heat with the container 88 and has evaporated is returned to the compressors A and B again, and the same cycle is repeated.

Next, an embodiment of the heat pump compressor will be described with reference to FIGS. 4 is a sectional view of the heat pump compressor, FIG. 5 is a sectional view taken along line VV of FIG. 4, FIG. 6 is a sectional view taken along line VI-VI of FIG. 4, and FIG. 7 is another embodiment of the heat pump compressor. An example cross section, FIG. 8 is a schematic diagram of a lubrication circuit.

The air conditioner 1 comprises two multi-vane compressors A and B arranged in the refrigerant circuit of the heat pump.
The compressors A and B are rotationally driven by the water-cooled engine 23. Here, one compressor A
Details of the configuration will be described with reference to FIGS. 4 to 6. Since the configuration of the other compressor B is the same as that of the compressor A, description thereof will be omitted.

A cap 300 for both compressor A and compressor B is fastened and fixed to the entire casing 100. Cases 1000 of the compressors A and B are housed in the entire casing 100, and cylinders 101 are further housed in the case 1000. Side blocks 102 and 103 are provided on both end surfaces of both cylinders 101, respectively. Further, in both cylinders 101, a rotor 104 is provided with a shaft portion 104 thereof.
a and 104b are rotatably provided by pivotally supporting the side blocks 103 and 102, and a large-diameter portion of the rotor 104 facing the cylinder 101 is, as shown in FIG.
Five slide grooves 105 are radially formed in the radial direction. Each slide groove 105 has a flat plate-shaped 5
When the vanes 106 are slidably fitted in the radial direction and the rotor 104 is rotating in the arrow direction,
The outer end of each vane 106 rotates while slidingly contacting the bore 101a having an elliptical cross section of the cylinder 101.

In the cylinder 101, there are formed two pressurizing chambers 107 which are partitioned by the rotor 104 and act by suction and compression to pressurize the refrigerant. As described above, the pressurizing chamber 107 includes the cylinder 10 that is at least two wall members.
1 and the rotor 104, and has a negative pressure portion 107a and a pressurizing portion 107b, and constitutes a pressurizing means E that pressurizes the refrigerant by moving one of the two wall members relative to the other. To be done. In this way, one of the cylinder 101 and the rotor 104 including the pressurizing means E is made stationary and the other is moved, while the other moving wall member is driven, and the drive device M having the lubrication portion is arranged. ing.

Further, the cylinder 101 is formed with a pair of suction passages 108 penetrating in the width direction. Suction ports 109 and 110 communicating with the negative pressure portion 107a of the pressurizing chamber 107 that performs suction compression are formed in the side blocks 102 and 103, respectively, and the suction port 110 is provided through a suction passage 108,
The suction ports 109 directly communicate with the upstream chambers 111, respectively. The upstream chamber 111 is formed between the side block 102 and each cap 300.

The cap 300 is provided with a suction port 600 communicating with the upstream chamber 111, and the suction port 600 is connected to a pipe 602 through a check valve 601. The pipe 602, the suction port 600, the upstream chamber 111, and the suction port Passage 108, suction port 1
09 and the suction port 110 communicate with the sub accumulator 56 and form a low pressure side refrigerant passage G for guiding the refrigerant from the low pressure circuit X in the refrigerant circuit 6 to the pressurizing chamber 107. Check valve 6
Reference numeral 01 allows a flow in the direction of the pressurizing chamber 107 in the middle of the low pressure side refrigerant passage G, and lubricates the low pressure refrigerant gas in the sub accumulator 56 from the low pressure circuit X via the low pressure side refrigerant passage G to lubricate the gas. The working oil is sucked by driving the compressors A and B, respectively.

In the cylinder 101, as shown in FIG.
Pressurizing unit 10 of each pressurizing chamber 107 that acts on each suction and compression.
7b are formed with discharge ports 112, and each of the discharge ports 112 has a pressurizing chamber 10 for suction and compression.
A valve 114 that allows the flow of the vapor-phase refrigerant from 7 to the discharge chamber 113 is provided.

Further, as shown in FIG. 4, the side block 103 has a holder 11 having an oil separator 115.
6 is provided by tightening and fixing with hexagon socket head bolts 117, and the side blocks 102, 103 and the casing 10 are provided.
Discharge chamber 113 formed between 0 and the cylinder 101
Communicates with the oil separator 115 via a discharge passage 118 that opens to them.

An oil sump 119 is formed on the inner side of the cylinder 101 in the casing 100, and a discharge port 120 formed in the casing 100 is opened at the upper part of the oil sump 119, and the discharge port 120 is formed. Piping 50
0 to the oil separator 52 arranged in the discharge side circuit 50. That is, the discharge port 112, the discharge chamber 113, the discharge passage 118, the oil separator 115, the oil sump 119, the discharge port 120, and the pipe 500 transfer the refrigerant discharged from the pressure chamber 107 to the high-pressure circuit Y in the refrigerant circuit 6. A high pressure side refrigerant passage I is formed to guide the high pressure refrigerant and lubricating oil.

The oil sump 119 also serves as a refrigerant high-pressure chamber, and the oil sump 119 collects lubricating oil. The oil sump 119 is disposed in at least one of the high pressure circuit Y and the high pressure side refrigerant passage I, and separates and stores the lubricating oil in the refrigerant pressurized in the oil sump 119.

Below the oil sump 119, the oil inlet 1 of the oil passage 121 formed in the side block 103 is provided.
21a is opened, and this oil passage 121 communicates with the shaft portion 104a of the rotor 104 so as to guide and lubricate the lubricating oil. Further, the oil passage 12 is provided in the side block 102.
2 is formed, and the oil passage 122 is formed in the shaft portion 1 of the rotor 104.
The lubricating oil that is in communication with the shaft portion 104a is guided to the gap between the side block 102 and the rotor 104 from the oil passage 122 and is lubricated. Further, oil passages 125 are formed at four locations in the cylinder 101. The oil passage 125 communicates with the oil passage 121 via the oil passage inlet 121b of the side block 102, the oil passage 125 communicates with the oil passage 126 of the side block 103, and the oil passage 125 further communicates with the oil passage 127. . The oil passage 126 is the cylinder 101.
The lubricating oil is guided from the oil passage 125 to the shaft portion 104b of the rotor 104 and communicates therewith. Further, the oil passage 127 is the rotor 104 of the shaft portion 104 b of the rotor 104.
The lubricating oil that is in communication with the base and is guided from the oil passage 126 is guided from the oil passage 127 to the gap between the side block 103 and the rotor 104 to be lubricated, and the negative pressure of the pressurizing chamber 107 that is suction-compressed. It is guided to the portion 107a. In this way, the oil passages 121, 122, 125, 126, 127, the gap between the side block 102 and the rotor 104, and the gap between the side block 103 and the rotor 104 are
The oil reservoir 119 constitutes a first oil passage K which connects the low pressure side refrigerant passage G in the compressors A and B and the low pressure refrigerant passage J formed of the low pressure circuit X, and the outlet thereof is the negative pressure portion 107a. Is. The first oil passage has a lubrication section N on the way.
Has been arranged.

An opening 128 is provided at the top of the casing 100.
Is covered with a transparent glass 129 to provide a peep window 130, and an oil inlet 131 is provided on the opposite side of the peek window 130. The injection bolt 132 is removed so that lubricating oil can be injected from the oil inlet 131. There is. Further, the bottom portion 100a of the casing 100 has a central portion 100b.
Is so slanted that the drain is contained in the lubricating oil in the central portion 100b. The oil drain outlet 13 is provided at the central portion 100b of the bottom portion 100a.
3 is provided to remove the drain bolt 134 to discharge the lubricating oil from the oil drain discharge port 133 to replace the oil, or to discharge only the drain at a predetermined time.

An oil discharge pipe 610 is attached to the lower part of the casing 100, and this oil discharge pipe 610 is connected via a pipe 611 to a pipe 612 for returning the lubricating oil of the oil separator 52 to the compressors A and B side. The lubricating oil in the oil sump 119 is sent to the pipe 612. The pipe 612 is the sub accumulator 56.
The low-pressure refrigerant gas inside and the lubricating oil are connected to the pipes 602 for returning to the compressors A and B, respectively.

The opening 610a of the oil discharge pipe 610 is set at a predetermined height inside the casing 100 to prevent drainage from being discharged, but is set at a position lower than the oil supply port 115a of the oil separator 115. To be done.

As described above, the second oil passage having the opening 610a disposed above the oil inlet 121a which is the oil reservoir side opening of the first oil passage K and communicating with the low-pressure refrigerant passage J is provided. L is arranged, and the second oil passage L is provided at an upstream side of the first oil passage K.
It communicates with the low-pressure refrigerant passage J.

Further, without using the oil discharge pipe 610,
The lubricating oil is directly piped from the bottom of the casing 100.
You may make it discharge from 11 and send to the piping 612.

As shown in FIG. 8 which functionally displays the configurations of FIGS. 4 to 6, the second passage communicating with the upstream side of the check valve 601 through the pipe 611 and the pipe 612 by the passage L1.
As another example of the oil passage L, the passages L2, L3, L
4 or L5 may be provided alone or in combination. That is, in the upstream portion of the negative pressure portion 107a, which is the outlet of the first oil passage K, the passage L2 has the pressure chamber 107
To the negative pressure portion 107a, the passage L3 to the upstream chamber 111, and the passage L4 to the upstream side or the downstream side of the check valve 601 by the passage L5.

In the embodiment shown in FIGS. 4 to 6, the second oil passage L includes the oil discharge pipe 610, the pipe 611, and the pipe 6.
12 and the pipe 602, and the first oil passage K
Lubricating oil is sent to the upstream side of the check valve 601 through the passage L1 in the upstream portion from the outlet. That is, the oil reservoir side opening 121a of the first oil passage K constitutes the oil suction port K10, and the oil reservoir side opening 610a of the second oil passage L constitutes the oil supply port L10.
The lubricating oil is the oil suction port K of the first oil passage K.
10, the lubricating portions of the bearings of the shaft portions 104a and 104b of the rotor 104, the rotor 104 and the side blocks 102,
It is supplied to the negative pressure section 107a of the pressurizing chamber 107 together with the refrigerant from the suction port of the wall from between the wall of 103. In addition, the second oil passage L includes the pipe 611 and the pipe 6.
12 is sent to the upstream side of the check valve 601 and the pipe 611 of the second oil passage L is communicated with the pipe 612 of the oil return passage from the oil separator 52 to the low pressure circuit X. The second oil passage L is a low pressure circuit X
Are returning to.

In the embodiment shown in FIG. 7, the second oil passage L is constituted by the pipe 620, and the lubricating oil is sent to the upstream chamber 111 by the passage L3 in the upstream portion of the first oil passage K. That is, the oil sump side opening 121a of the first oil passage K constitutes the oil suction port L10, and the oil sump side opening 610a of the second oil passage L.
Constitutes the oil supply port L10.

An electromagnetic clutch 43 is provided at the end of each rotor 104 of the compressors A and B, and the driving force of the water-cooled engine 23 is ON / OFF of the electromagnetic clutch 43.
Is selectively transmitted to the rotor 104 by. And
When power is transmitted to the rotor 104 and is rotationally driven, the vanes 106 rotate integrally.
No. 06 projects radially outward along the slide groove 105 due to centrifugal force, and the tip end portion of the bore 101 of the cylinder 101.
Rotating while sliding on a, the upstream chamber 111, the suction port 109
Further, the gas-phase refrigerant sucked into the pressurizing chamber 107 in the cylinder 101 through the suction port 110 through the suction passage 108 is
The lubricating oil compressed by the vane 106 and sucked into the pressurizing chamber 107 through the first oil passage K and the second oil passage L lubricates the sliding contact portion between the vane 106 and the bore 101, and The high-pressure gas-phase refrigerant and the lubricating oil are discharged through the discharge port 112 and the valve 114 into the discharge chamber 113.
Is discharged to. The vapor-phase refrigerant and the lubricating oil discharged to the discharge chamber 113 reach the oil separator 115 via the discharge passage 118, and the gas-phase refrigerant after the oil component is removed there flows into the oil sump 119 and finally Outlet 12
From 0 to the discharge side circuit 50 outside the machine. On the other hand, the lubricating oil flows from the oil separator 115 to the oil sump 1
19 Drop down.

Thus, the lubricating oil of the compressors A and B exchanges heat with the liquid-phase refrigerant from the sub accumulator 56,
As a result, a dedicated radiator for cooling the lubricating oil is unnecessary, and the cost can be reduced accordingly. In the middle of the first oil passage K, the lubricating oil lubricates the bearing portions 104a and 104b and the lubricating portion N such as the sliding portions of the rotor 104 with the side blocks 102 and 103. Further, an oil passage may be provided in the rotor 104 to connect the oil passage 126 to the bottom of the slide groove 105, so that the vane 106 can be more effectively lubricated against sliding in the slide groove.

When the operation is stopped, the low-temperature low-pressure vapor-phase refrigerant in the low-pressure refrigerant passage J is condensed before the high-temperature high-pressure vapor-phase refrigerant, so that the first oil passage K and the second oil are discharged. A differential pressure is generated at both ends of both oil passages of the passage L, and the lubricating oil from the oil reservoir 119 passes through the first oil passage K, and the lubricating oil flows from the pressurizing chamber 107 to the upstream chamber 111, and the second The lubricating oil passing through the oil passage L directly flows to the low pressure refrigerant passage J. But the second
When the opening L10 of the oil passage L comes out of the oil surface, the high-pressure-side refrigerant flows through the second oil passage L to the low-pressure refrigerant passage J. This is because the gas refrigerant, which has a lower viscosity than the lubricating oil, is more likely to flow. Therefore, a larger amount of the lubricating oil flows in the first oil passage K, and the differential pressure between both ends of both oil passages is immediately lost. The flow of the lubricating oil in the first oil passage K is stopped, and the lubricating oil having an oil level of the height between the opening K10 of the first oil passage K and the opening L10 of the second oil passage L is accumulated in the oil. 119 remains.

For this reason, when the compressors A and B are re-driven, a differential pressure is generated in both oil passages K and L, and the refrigerant passes through the second oil passage L, but lubrication occurs through the first oil passage K. Since the working oil flows, the initial poor lubrication can be eliminated. After that, the lubricating oil that has flowed out to the low-pressure refrigerant passage J when the operation is stopped returns to the oil reservoir 119, and the oil level returns to a position above the opening L10 of the second oil passage L.

After re-driving the compressors A and B, the first
Since the communication portion of the oil passage K to the low-pressure side refrigerant passage G is close to the pressurizing chamber 107, the negative pressure is large, so that the first oil passage K
The side has a larger differential pressure at both ends. Therefore, even if the refrigerant passes through the second oil passage L, more lubricating oil flows through the first oil passage K.

The middle part of the second oil passage L may be constructed by a pipe passing outside the compressors A and B, or the total length of the second oil passage L may be equal to that of the compressors A and B. It may be configured to pass through. Further, the lubricating portion N may be passed in the middle of the second oil passage L.

Further, as shown in FIG. 9, the first oil passage K and the second oil passage L are integrated, that is, one oil passage P, and the oil reservoir 119 of this oil passage P is formed.
There may be two side openings, and the openings L10 and K10 may be upper and lower. As the lubricating oil flows through the oil passage P, the oil level in the oil sump 119 lowers, and when the opening L10 is exposed on the oil level, the vapor phase liquid medium passes through the oil path P from the opening L10. The amount of oil flowing is reduced by that amount, and the differential pressure in the oil passage P can be set to 0 before the oil level drops to the opening L10.

Further, the oil passage P is, in this embodiment,
The check valve 700 communicates with the negative pressure portion 107a of the pressurizing chamber 107, but the check valve 700 does not necessarily have to be provided. Further, the oil passage P may communicate with the upstream chamber 111.

When the compressors A and B are driven again, a differential pressure is generated in the oil passage P, the mixed fluid of the lubricating oil and the vapor phase refrigerant flows into the low pressure refrigerant passage J, and the pressurizing chamber 107 is lubricated. By connecting the outlet side of the second oil passage L to the downstream side of the check valve 601 like L2, L3, or L5, when the compressor is stopped, the low pressure from the oil reservoir 119 passes through the second oil passage L. Even if it flows out to the side refrigerant passage G, it does not flow out to the low-pressure circuit X that is upstream thereof, so that the rotor 10
When 4 is re-rotated to re-drive the compressors A and B, the lubricating oil that has flowed out is quickly sucked into the negative pressure portion 107a, and after lubricating the pressurizing means E, it quickly returns to the oil sump 119. On the other hand, when the first oil passage K re-drives the compressors A and B,
It is immediately supplied to the bearing portions 104a and 104b, and then sucked into the negative pressure portion 107a. That is, lubrication is smoothly performed.

When the outlet side of the second oil passage L communicates with the upstream side of the check valve 601 like L1 or L4, the lubricating oil flowing out to the low pressure circuit X is added when the compressor A is re-driven. When the amount of oil outflow is large, the vane 106 can be prevented from being damaged by liquid compression during re-driving, which is a problem when a large amount of oil flows out.

Although not stated in the claims, the second
Opening L10 'on the oil reservoir 119 side of the oil passage L of
Is located above the oil level, and an opening / closing valve 1001 is arranged in the middle of the second oil passage L so that the opening / closing valve 1001 is opened when the compressors A and B are stopped and closed when driven. You can In this case, the on-off valve 1001 may be an electromagnetic valve, or may be a valve that opens and closes by using the pressure on the high pressure side, which changes greatly when the compressor is driven or stopped by the diaphragm. As a result, the oil level in the oil sump 119 does not decrease. Further, in this case, when the first and second oil passages K and L are connected to the low pressure side refrigerant passage G on the downstream side of the check valve 601, the differential pressure can be eliminated in a short time.

[0072]

As described above, according to the first aspect of the invention, the first oil passage has the opening arranged at a position higher than the oil reservoir side opening, and the second oil passage communicates with the low pressure refrigerant passage. Since the oil passage is arranged and the second oil passage is communicated with the low-pressure refrigerant passage, the operation stop causes a differential pressure at both ends of both the first oil passage and the second oil passage. Although the refrigerant passes through the second oil passage, the lubricating oil flows through the first oil passage, so that the initial lubrication failure can be eliminated, and then the lubricating oil flowing out to the low-pressure refrigerant passage at the time of operation stop is Returning to the oil sump, the oil level returns to the upper part of the opening of the second oil passage, so that lubrication can be smoothly performed when the operation is performed again.

According to a second aspect of the present invention, one of the wall members is made stationary and the other is moved, and the other moving wall member is driven, and a drive device having a lubricating portion is arranged. By disposing the lubricating portion in the middle of the oil passage, the lubricating oil from the oil sump is guided to the low pressure side refrigerant passage after passing through the lubricating portion, so that the oil sump side opening of the first oil passage is formed. Is low, the lubricating oil that enters the first oil passage from this opening flows out to the low-pressure refrigerant passage through the lubrication portion when the compressor is restarted, and this lubricating oil is further compressed. It is possible to lubricate not only the pressure chamber but also the lubrication part smoothly.

According to a third aspect of the present invention, a check valve which allows a flow in the direction of the pressurizing chamber is disposed in the middle of the low pressure side refrigerant passage, and at least the second oil passage is provided downstream of the check valve. Therefore, when the compressor is stopped, the lubricating oil flowing out to the low-pressure side refrigerant passage through the second oil passage lubricates the pressurizing chamber quickly at the time of re-driving and returns to the oil sump.

According to a fourth aspect of the present invention, the first oil passage and the second oil passage are integrated into one oil passage, and two openings on the oil reservoir side of the oil passage are provided. Even if the operation is stopped, the lubricating oil flows through the oil passage to lower the oil level and expose the second opening above the oil level even if the operation is stopped. , The lubricating oil is guided to the oil passage from the l-th opening and flows to the low-pressure refrigerant passage in the gas-liquid mixed state, and the differential pressure disappears, and the first opening and the second opening
When the compressor is driven again, a differential pressure is generated in the oil passage, and the mixed fluid of oil and gas-phase refrigerant flows into the low-pressure refrigerant passage, which lubricates the pressurizing chamber. With a simple and compact structure, it is possible to smoothly perform lubrication at the time of re-operation, and it is possible to keep the lubricating oil in the oil reservoir constant.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram of an air conditioner.

FIG. 2 is a schematic configuration diagram of the air conditioner during a cooling operation.

FIG. 3 is a schematic configuration diagram during heating operation of the air conditioner.

FIG. 4 is a cross-sectional view of a heat pump compressor.

FIG. 5 is a sectional view taken along the line VV of FIG. 4;

FIG. 6 is a sectional view taken along the line VI-VI of FIG. 4;

FIG. 7 is a cross-sectional view of another embodiment of the heat pump compressor.

FIG. 8 is a schematic diagram of a lubrication circuit.

FIG. 9 is a schematic view of a lubricating circuit of another embodiment of the heat pump compressor.

[Explanation of symbols]

 6 Refrigerant circuit 107 Pressurizing chamber 119 Oil sump A, B Compressor E Pressurizing means K First oil passage K10 Oil sump side opening of first oil passage K L Second oil passage L10 Second oil passage L Oil sump side opening

Claims (4)

[Claims] 1. A pressurizing chamber that is disposed in the middle of a refrigerant circuit of a heat pump and is formed inside at least two wall members, and pressurizes a refrigerant, and one of the two wall members is opposed to the other. Means for pressurizing the refrigerant by exercising mechanically, a low pressure side refrigerant passage for guiding the refrigerant from the low pressure circuit in the refrigerant circuit to the pressurizing chamber, and the refrigerant discharged from the pressurizing chamber as the refrigerant. An oil having a compressor having a high-pressure side refrigerant passage leading to a high-pressure circuit in the circuit, and separating and storing lubricating oil in the refrigerant pressurized in at least one of the high-pressure circuit or the high-pressure side refrigerant passage In a lubricating device for a heat pump compressor, in which a sump is arranged, and a first oil passage communicating with the oil sump and the low-pressure side refrigerant passage in the compressor and the low-pressure side refrigerant passage formed of the low-pressure circuit are arranged, Has an opening disposed in the upper position than the oil reservoir side opening of the first oil passage, the heat pump compressor, characterized in that a second oil passage communicating with said low-pressure refrigerant passage. 2. One of the wall members is stationary, the other is moved, and the other moving wall member is driven, and a drive device having a lubrication portion is disposed, and the middle of the first oil passage is provided. By arranging the lubrication part in
The heat pump compressor according to claim 1, wherein the lubricating oil from the oil reservoir is introduced into the low-pressure refrigerant passage after passing through the lubricating portion. 3. A check valve for permitting a flow in the direction of the pressurizing chamber is disposed in the middle of the low pressure side refrigerant passage, and at least the second oil passage is connected downstream of the check valve. The compressor for a heat pump according to claim 1 or 2, characterized in that. 4. The first oil passage and the second oil passage are integrated into one oil passage, and two openings are provided on the oil reservoir side of the oil passage. The first opening and the second opening The heat pump compressor according to any one of claims 1 to 3, wherein the positions of the openings are set up and down.