JP2002098081A - Multistage compression type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a multistage compression type compressor capable of realizing high volumetric efficiency while reducing pressure loss even in the case of a refrigerant of high working pressure. SOLUTION: This multistage compression type compressor is provided with a motor element 14 and first and second compression elements 32, 34 driven by the motor element 14, inside a closed container 12. The first compression element 32 is provided with a discharge port 41 for discharging compressed refrigerant gas, and the second compression element 34 is provided with a discharge port 39 for discharging the refrigerant gas discharged from the discharge port 41 of the first compression element 32, sucked into the second compression element 34 and compressed therein. The discharge port 39 of the second compression element 34 is made smaller than the discharge port 41 of the first compression element 32.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-stage compression compressor in which refrigerant gas compressed and discharged by a first compression element is sucked into a second compression element, compressed and discharged.

[0002]

2. Description of the Related Art Conventionally, in a multistage compression type compressor of this type, when a refrigerant having a large difference between high and low pressures, for example, carbon dioxide (CO ₂ ) as an example of carbon dioxide, is used as a refrigerant, the refrigerant pressure becomes high. About 100k with compression element
g / cm ² G, while reaching about 30 kg / cm ² G for the first compression element on the lower stage side. As a result, the height difference was as large as about 70 kg / cm ² G, but there was almost no difference between the discharge port diameter of the first compression element and the discharge port diameter of the second compression element of the multistage compression type compressor.

[0003]

In such a multistage compression type compressor, the rejection volume of the second compression element in which the refrigerant pressure is high is smaller than the rejection volume of the first compression element in which the refrigerant pressure is low. When the first compression element and the second compression element have the same discharge port diameter, the first compression element has a larger volume flow rate, so that a pressure loss occurs here. For this reason, there was a problem that the volume efficiency of the first compression element was significantly deteriorated.

When the discharge port diameter of the second compression element is set to a size corresponding to the port diameter of the first compression element, especially when a refrigerant having a high working pressure is used, the second compression element There was also a problem that the dead volume of a large.

SUMMARY OF THE INVENTION The present invention has been made to solve the problems of the prior art, and has a multistage structure capable of realizing high volumetric efficiency by reducing pressure loss even in the case of a refrigerant having a high working pressure. It is an object to provide a compression compressor.

[0006]

That is, a multi-stage compression type compressor according to the present invention includes an electric element in a closed container, and first and second compression elements driven by the electric element.
The refrigerant gas compressed and discharged by the compression element is sucked into the second compression element, compressed and discharged.
The discharge port of the compression element is smaller than the discharge port of the first compression element.

Further, in the multistage compression type compressor according to claim 2, the excluded volume of the second compression element is set to 55% or more and 85% or less of the excluded volume of the first compression element.

According to the present invention, an electric element and a first and a second compression element driven by the electric element are provided in the closed container, and the refrigerant gas compressed and discharged by the first compression element is provided. Is sucked into the second compression element, and the discharge port of the second compression element is smaller than the discharge port of the first compression element of the multi-stage compression type compressor that discharges the compressed air.
For example, the displacement volume of the second compression element is defined as
Refrigerant gas discharged from the discharge port of the first compression element with respect to refrigerant gas discharged from the discharge port of the second compression element by setting the excluded volume of the first compression element to 55% or more and 85% or less. Even when the discharge amount of the first compression element increases, it is possible to suppress an increase in the pressure loss of the first compression element, and at the same time, it is possible to reduce the dead volume of the second compression element. . Therefore, the pressure loss of the first compression element can be greatly reduced, and high volume efficiency can be realized.

[0009]

Next, an embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional side view of a two-stage compression type compressor 10 having first and second compression elements 32 and 34 as an embodiment of the multi-stage compression type compressor of the present invention.
2 shows plan views of the two-stage compression type compressor 10 of FIG. In the figure, reference numeral 10 denotes a two-stage compression type compressor as a multi-stage compression type compressor.
The rotary compression mechanism 18 includes an electric element 14 disposed and housed in the internal space of the closed container 12 and a first compression element 32 and a second compression element 34 driven by the rotation shaft 16 of the electric element 14. It is configured.

The hermetically sealed container 12 has an oil reservoir at the bottom and a container body 1 for housing the electric element 14 and the rotary compression mechanism 18.
2A and a bowl-shaped lid 12B for closing the upper opening of the container body 12A.
2B is provided with a terminal terminal (wiring omitted) 20 for supplying electric power to the electric element 14.

The electric element 14 has a stator 22 mounted annularly along the inner peripheral surface of the upper space of the closed casing 12.
And a rotor 24 inserted and arranged with a slight gap provided inside the stator 22. The rotor 24 is fixed to the rotating shaft 16 that extends vertically through the center.

The stator 22 has a laminated body 26 in which ring-shaped electromagnetic steel sheets are laminated, and a stator coil 28 wound around the laminated body 26. Further, the rotor 24 is also formed of a laminated body 30 of electromagnetic steel sheets similarly to the stator 22, and the both constitute an AC motor. Instead of an AC motor, a DC motor in which a permanent magnet is embedded in a rotor can be used.

An intermediate partition plate 36 is sandwiched between the first compression element 32 and the second compression element 34. That is, the first compression element 32 and the second compression element 34 are composed of an intermediate partition plate 36, cylinders 38 and 40 arranged above and below the intermediate partition plate 36, and the upper and lower cylinders 3.
The upper and lower rollers 46 and 48 which are fitted to the upper and lower eccentric portions 42 and 44 provided on the rotary shaft 16 with a phase difference of 180 degrees inside the inner and outer surfaces of the upper and lower rollers 46 and 48 and contact the upper and lower rollers 46 and 48. And the upper and lower cylinders 38 and 40 respectively
8A, 40A and upper and lower vanes 50, 52, which are partitioned into high pressure chamber sides 38B, 40B, and upper and lower cylinders 38, 40.
Each of the support members (the upper support member 54 and the lower support member 56) which closes each opening surface and also serves as a bearing for the rotary shaft 16.

Upper support member 54 and lower support member 56
Are formed with suction passages 58, 60 and discharge muffling chambers 62, 64 which are appropriately communicated with the insides of the upper and lower cylinders 38, 40, and the openings of these discharge muffling chambers 62, 64 are closed by covers, respectively. . That is, the discharge muffling chamber 62 is closed by the upper cover 66 as a cover, and the discharge muffling chamber 64 is closed by the lower cover 68 as a cover. The discharge muffle chamber 64 and the electric element 14 side of the upper cover 66 in the closed container 12 are communicated with each other through a communication passage 63.

The upper cover 66 closes the opening of the discharge muffling chamber 62 communicating with the inside of the cylinder 38 of the second compression element 34, so that the inside of the sealed container 12 is closed.
Divide the four sides. The upper cover 66 has a thick portion 66A,
It is composed of a thin portion 66B other than the thick portion 66A (FIGS. 3 and 4). The thick portion 66A protrudes toward the electric element 14 from the thin portion 66B to enhance the deformation strength of the thick portion 66A than the thin portion 66B.

That is, in the upper cover 66, a portion (thick portion 66A) corresponding to the discharge muffling chamber 62 on the high pressure side (the second compression element 34) is made thicker than other portions (thin portion 66B). Therefore, when the pressure in the discharge muffling chamber 62 becomes high, the upper cover 66 is prevented from being deformed toward the electric element 14,
Two-stage compression type compressor 10 with minimum necessary thickness
The weight has been reduced. By providing the thick portion 66A in the upper cover 66, the rigidity of the upper cover 66 is greatly increased, and the area of the upper cover 66 is large even when the pressure difference between the discharge muffling chamber 62 and the electric element 14 is large. This prevents the thick portion 66A from being deformed. Also, by significantly increasing the rigidity of the upper cover 66,
Problems such as re-compression of the leakage of the refrigerant gas from the discharge muffling chamber 62 to cause an increase in the input are prevented.

The upper cover 66 is provided with a plurality of screw holes 67A for fixing the upper cover 66. The screw holes 67A allow the upper cover 66 to be connected to the discharge muffling chamber 6.
It is formed in a step portion 67 having a step recessed to the second side. That is, the upper cover 66 is provided with a stepped portion 67 that is recessed and formed lower than the thick portion 66A on the side of the discharge muffler chamber 62,
The step 67 has a screw hole 67A. The step 67 is substantially the same as the head of a mounting bolt 78 described later. By providing the step 67 on the upper cover 66, the mounting bolt 78 is prevented from protruding from the thick portion 66A. The step portion 67 is formed thinner on the side of the discharge muffling chamber 62 than the thick portion 66A, and the thin portion 66B and the step portion 67 may have the same thickness.
Further, if the head of the mounting bolt 78 is slightly smaller than the thick portion 66A, it may be projected. Thereby, the electric element 1
The insulation distance from the compressor 4 can be designed in the same manner as in the related art, so that the size of the entire two-stage compression type compressor 10 does not need to be increased.

The upper support member 54 and the lower support member 56
Are provided with discharge ports 39, 4 for communicating the insides of the cylinders 38, 40 with the discharge muffling chambers 62, 64 (recesses 121, 131).
1 is provided (FIGS. 5, 6, 7, and 8). The discharge ports 39 and 41 are formed on the discharge muffling chamber 62 and 64 sides with concave portions 121 and 131 formed in a predetermined shape, and the discharge ports 39 and 41 are opened in the concave portions 121 and 131. The discharge ports 39 and 41 are provided substantially in contact with a vane described later, and around the discharge ports 39 and 41, a valve seat 39A having a larger diameter than the discharge ports 39 and 41,
41A is provided.

The valve seats 39A and 41A are provided with concave portions 121 and 13 respectively.
1 (discharge muffling chambers 62, 64), the valve seats 39A, 41A are provided with valve bodies 122, 13 made of an elastic member made of a metal plate having a vertically long and substantially rectangular shape.
2 are in contact with each other and are in close contact with each other (see FIGS. 6, 8, and 1).
1). The valve bodies 122, 132 are provided with double stoppers 123, 133 having substantially the same shape as the valve bodies 122, 132, and the valve bodies 122, 132 and the stoppers 123, 133 are provided.
The other side is provided with discharge ports 39, 4 in the recesses 121, 131.
1 and screw holes 125 and 13 provided at a predetermined interval.
5 is fixed with screws 124 and 134.

The stoppers 123 and 133 are connected to the valve body 12.
2, 132, which is thicker and stronger than the other side, and the valve body 12 becomes closer to one side (valve seat 39A, 41A side) than the other side.
It has a curved shape that is further away from 2,132. That is, when one side of the valve bodies 122 and 132 is elastically separated from the valve seats 39A and 41A, the stoppers 123 and 133 are turned off.
22 and 132 are prevented from being deformed beyond the elastic limit. Further, the valve bodies 122 and 132 abut against valve seats 39A and 41A formed around the discharge ports 39 and 41 with a constant urging force to close and open and close the discharge ports 39 and 41 with elastic force.

The discharge ports 39 and 41 are provided in valve seats 39A and 41A as shown in FIGS. 5, 6, 7, and 8, respectively. These discharge ports 39, 41 are provided with valve seats 39A,
It is provided at a position deviated from the center of 41A, and one side of the discharge ports 39 and 41 is provided substantially in contact with a vane described later (solid lines in FIGS. 9 and 10). That is, the discharge ports 39 and 41 are displaced in the circumferential direction around the centers of the cylinders 38 and 40. In this case, if the ejection ports are larger than the ejection ports 39 and 41, the lead lines are shifted to the positions of the ejection ports 39 and 41 indicated by dotted lines.

Thus, the cylinder 38, the cylinder 40
The inside is partitioned by the vanes 50 and 52 into a low-pressure chamber side 38A, 40A and a high-pressure chamber side 38B, 40B.
Pressure loss of the refrigerant gas compressed at 40B is prevented.
When the discharge ports 39, 41 are separated from the vane, even if the refrigerant gas compressed in the cylinders 38, 40 is discharged from the discharge ports 39, 41, the refrigerant gas remains between the discharge ports 39, 41 and the vane. Since the efficiency is reduced, the discharge ports 39 and 41 are brought as close as possible to the vane to improve the compression efficiency.

The discharge ports 39 and 41 are connected to the valve seat 39.
The diameter can be enlarged and reduced within A and 41A, and the position can be changed. Thus, the diameter of the discharge ports 39 and 41 can be enlarged and reduced, and the position can be changed without changing the positions of the valve seats 39A and 41A. Therefore, the first and second compression elements 32 can be changed simply by changing the diameter of the discharge ports 39 and 41 and changing the positions without greatly changing the molding dies of the upper support member 54 and the lower support member 56. , 34 can be freely changed, and the two-stage compression type compressor 10 can be freely designed.

The discharge port 39 provided on the second compression element 34 is connected to the discharge port 41 provided on the first compression element 32.
It has a smaller diameter than that. This is the second compression element 3
This corresponds to a situation where the volume flow rate of the refrigerant gas discharged from the discharge port 41 of the first compression element 32 is larger than the volume flow rate of the refrigerant gas discharged from the discharge port 39 of No. 4. Further, the excluded volume of the second compression element 34 is set to be 55% or more and 85% or less of the excluded volume of the first compression element 32.

That is, since the diameter of the discharge port 39 of the second high-pressure compression element 34 is smaller than the diameter of the discharge port 41 of the low-pressure first compression element 32, the pressure loss of the first compression element 32 is reduced. Thus, the performance of the two-stage compression type compressor 10 can be maximized. Also, by reducing the pressure loss, the first compression element 32 and the second compression element 3
Since the compression balance of the compressor 4 is also uniform, vibrations due to torque fluctuations of the two-stage compression compressor 10 can be effectively reduced, and efficiency can be improved.

In the upper support member 54 and the lower support member 56, R-surfaces 54B are provided at the corners of the discharge muffling chamber 62 (concave part 121) and the discharge muffling chamber 64 (concave part 131) and the bearings 54A, 56A. , 56B (FIGS. 12, 13, 14, and 15). by this,
Bearing 54A of upper support member 54, lower support member 56,
The reinforcement strength of 56A is reinforced. That is, the upper and lower support members 54 and 56 have the discharge muffling chamber 62 (the concave portion 1).
21), the discharge muffling chamber 64 (the recess 131) and the bearing 54
At the corners of the upper support member 54 and the lower support member 56 with the bearings 54A and 56A, the corners with the A and 56A are easily deformed due to stress concentration.
B, 56B, thereby providing bearings 54A, 56A
Is prevented from falling down.

On the other hand, the cylinder 38 is engraved with a vertically long rectangular storage portion 70A for storing the spring 76. The storage portion 70A is formed orthogonal to the guide groove 70 and the guide groove 70 side is formed. Open (FIGS. 16 and 1
7). And the storage part 70 carved in the cylinder 38
A communicates with the guide groove 70 and is open in the axial direction of the rotating shaft 16. The open part 70B of the storage part 70A is located on the side of the intermediate partition plate 36 and is closed by the intermediate partition plate 36. When the storage section 70A is provided by engraving the surface of the cylinder 38 opposite to the intermediate partition plate 36 side, the opening 70A of the storage section 70A is closed by the support member 54.

Further, the spring 76 is constituted by a vertically long, substantially rectangular plate spring as a spring member (FIG. 18). One end of the spring 76 has a vane 5 as a vane.
A curved pressing pressure portion 76A whose outer periphery is in contact with 0 is formed, and the other end is fixed in the storage portion 70A. The vane 50 is reciprocally disposed and housed in a guide groove 70 formed in the outer diameter direction in the cylinder 38. With the other end of the spring 76 fixed in the housing part 70A, the vane 50 is pressed. Urges the vane 50 toward the roller 46 (FIG. 20). Thus, the vane 50 is always in contact with the roller 46 by the urging force of the spring 76.

Further, the surface roughness of the guide groove 70 of the vane 50 is finished with high precision, and the vane 50 and the guide groove 70
To improve adhesion. Thereby, the leakage of the high-pressure refrigerant gas from between the vane 50 and the guide groove 70 is reduced, and the volume efficiency of the two-stage compression type compressor 10 is improved. Further, the vanes 50 contacting the guide grooves 70
By finishing the surface roughness of the vane with high precision, the vane 50
The effect of reducing the refrigerant gas leaking from between the guide groove 70 and the groove can be increased, the leakage of the refrigerant gas can be further reduced, and the volume efficiency of the compressor 10 can be improved.

FIG. 19 shows a vane 52 as a vane.
Is shown. The vane 52 is reciprocally disposed and housed in a guide groove 72 carved in the outer diameter direction in the cylinder 40. Then, a spring hole 7 is provided in the radial direction of the cylinder 40.
A spring 77 made of a coil spring is inserted into the spring hole 72A from the outside of the cylinder 40 as a spring member, and a lid 77A is inserted and fixed to the rear side of the spring 77. Thereby, the vane 52 is always in contact with the roller 48 by the urging force of the spring 77. The vane 52 is provided with a storage part 70A similarly to the vane 50, and a spring 76 made of a leaf spring fixed in the storage part 70A is provided.
The roller 48 may always be brought into contact with the biasing force of.

On the other hand, among the elements constituting the rotary compression mechanism 18, the upper support member 54, the cylinder 38,
Intermediate partition plate 36, cylinder 40 and lower support member 56
Are arranged in this order, and are integrally connected and fixed together with the upper cover 66 and the lower cover 68 using a plurality of mounting bolts 78. At this time, since the stepped portion 67 is provided on the upper cover 66, the mounting bolt 78 does not protrude from the thick portion 66A, so that the rotary compression mechanism 18 can be moved toward the electric element 14 by that amount, and the two-stage compression can be performed. The size of the type compressor 10 can be reduced. In addition, both vanes 50, 5
A plurality of mounting bolts 78A are added near 2 (in this case, 2
In this way, the lower cover 68 is integrally connected and fixed from the upper cover 66. Thereby, the deformation of the components constituting the second compression element 34 can be suppressed, and a decrease in efficiency due to the refrigerant gas leak generated by the deformation of the components can be suppressed.

As shown in FIG. 21, a vertical oil hole 80 is formed in the lower part of the rotary shaft 16 at the center of the shaft, and horizontal oil supply holes 82 and 84 are formed in the oil hole 80.

By the way, the connecting portion 90 for connecting the upper and lower eccentric portions 42 and 44 formed integrally with the rotary shaft 16 with a phase difference of 180 degrees has a sectional shape of the rotary shaft 16.
In order to increase rigidity by making the cross-sectional area larger than the circular cross-section, the upper, lower, left, and right sides are substantially symmetrical, for example, like a non-circular rugby ball (FIG. 22). The connecting portion 90 for connecting the vertical eccentric portions 42 and 44 provided on the rotary shaft 16 is coaxial with the rotary shaft 16, but has a sectional shape of the vertical eccentric portion 4.
The thickness in the direction perpendicular to the eccentric direction is larger than the thickness in the eccentric direction of 2, 44.

As a result, the cross-sectional area of the connecting portion 90 connecting the upper and lower eccentric portions 42 and 44 provided integrally with the rotating shaft 16 is increased, the second moment of area is increased, and the strength (rigidity) is increased, and the durability is increased. And improve reliability. Specifically, when a refrigerant having a particularly high working pressure, which will be described below, is subjected to two-stage compression, the pressure difference between the high and low pressures is large.
However, the strength (rigidity) of the connecting portion 90 is increased by increasing the cross-sectional area, thereby preventing the rotating shaft 16 from being elastically deformed.

In this embodiment, carbon dioxide (CO ₂ ) as an example of carbon dioxide, which is a natural refrigerant in consideration of flammability and toxicity, is friendly to the global environment as a refrigerant.
As the oil as a lubricating oil, existing oils such as mineral oil (mineral oil), alkylbenzene oil, ether oil and ester oil are used.

On the other hand, it is well known that carbon bearings provide higher reliability than iron, and it is also well known that carbon dioxide (CO ₂ ) is easily combined with moisture. Therefore, the upper support member 54 and the lower support member 56
The bearings 54A and 56A with the rotating shaft 16 are made of carbon material. And 100 pp in CO ₂ refrigerant
m or more (usually 100 ppm) of water is added. That is,
Since the carbon bearings (bearings 54A and 56A of the upper support member 54 and the lower support member 56) usually contain moisture, C
By including a predetermined amount of water in O ₂ , the bearing performance can be greatly improved.

The upper support member 54 and the lower support member 5
6 includes suction passages 58, 60 and discharge muffling chambers 62, 64.
The refrigerant introduction pipes 92 and 94 for introducing the refrigerant gas to the upper and lower cylinders 38 and 40 via the refrigeration pipes are connected to the refrigerant discharge pipes 96 and 98 for discharging the compressed refrigerant gas.

Refrigerant introduction pipes 92 and 94 and refrigerant discharge pipe 9
6, 98 are fixed to the collar 143 as shown in FIG.
The collar 143 is connected to the upper support member 5 via the tube 142.
4. The tube 142 is fixed to the lower support member 56, and the tube 142 is inserted and fixed in the sleeve 140 fixed to the closed container 12. The main body 140A of the sleeve 140 is formed of a metal such as iron into a cylindrical shape having a predetermined length, and a small-diameter portion 141 having a smaller diameter than one side is formed on one side with a predetermined length (FIG. 2).
4, FIG. 25), the small-diameter portion 141 is fixed to the closed container 12 by welding or the like.

The tube 142 is also made of a metal such as iron and has a cylindrical shape having a predetermined length, and a main body 142A having a predetermined diameter as shown in FIG.
B. Body 142A of tube 142
Is formed to have a smaller diameter than the body 140A of the sleeve 140, and the body 142A of the tube 142 is
0 body 140A. In this case, one side of the tube 142 is squeezed so that the small-diameter portion 142 having a predetermined length
B is formed, and the small diameter portion 142B is press-fitted and fixed to insertion holes provided in the upper support member 54 and the lower support member 56 (not shown).

The collar 143 is also formed of a metal such as iron into a cylindrical shape having a predetermined length, and the main body 144 is formed from one side in the order of a small diameter part 144A, a medium diameter part 144B, a large diameter part 144C and the other side. (FIG. 27). And the small diameter part 144
A is formed to have an outer diameter and a length dimension that can be pressed into the small diameter portion 142B of the tube 142, and the main body 142 of the tube 142
It is press-fitted and fixed to the small diameter portion 142B from the A side. Medium diameter part 14
4B is formed to have a larger diameter than the small diameter portion 144A, a smaller diameter than the tube 142 main body 142A, and a sleeve 140B.
It has the same length dimension as that of. In addition, color 143
The large diameter portion C is larger in diameter than the middle diameter portion 144B and
It has a shape that can be pressed into the main body 142A.

The middle diameter portion 144B is provided with a through hole 145 having a very small diameter as a fine hole. The through hole 145 penetrates the inside and outside of the main body 144 of the collar 143. Thus, the inside and outside of the main body 144 of the collar 143 are communicated. When inserted into the tube 142 main body 142A from the small diameter portion 142B side of the collar 143, the small diameter portion 14 of the collar 143 is inserted into the small diameter portion 141 of the tube 142.
2B is press-fitted and fixed, and the large-diameter portion C of the collar 143 is press-fitted and fixed in the main body 142A of the tube 142. Thereby, the circumference of the middle diameter portion 144B of the collar 143 and the tube 1
A predetermined space 1 as an interval between the main bodies 142A
46 are formed.

Then, the other end of the tube 142 (the small-diameter portion 1) from the open end of the sleeve 140 (the side away from the closed container 12).
A welded portion 1 in which a range extending from the main body 142A) on the separation side of 42B to the large-diameter portion 144C peripheral wall surface via the collar 143 is welded.
47 closes a space 146 between the collar 143 and the tube 142. That is, the sleeve 140 body 14
The tube 142 and the collar 143 are sequentially inserted and fixed by welding into the inside of the sleeve 0A, so that a space 146 at a predetermined interval is provided between the tube 142 and the collar 143 in the sleeve 140, and the space 146 is formed with a through hole 145.
Thereby, it communicates with the inside of the main body 144 of the collar 143.

The range from the open end of the sleeve 140 to the wall around the large diameter portion 144C of the collar 143 via the other end of the tube 142 is welded, but the air in the space 146 expands due to the heat during welding. As a result, a blowout hole is opened from the welded portion 147. This allows the space 146
And the outside communicate with each other, and the refrigerant gas leaks from the inside of the collar 143. However, since the through hole 145 communicating with the inside of the collar 143 main body 144 is provided in the middle diameter portion 144B, the inside of the space 146 is not provided. The expanded air is released into the main body 144 of the collar 143 through the through hole 145.

As a result, incomplete welding in which the expanded air in the space 146 blows out from the welded portion 147 to form a hole is also eliminated, so that the space 146 communicates with the outside of the collar 143. Welded part 1 without any trouble
47 can be sealed. That is, the middle diameter portion 144 of the collar 143
B allows the inflated air in the space 146 to escape into the main body 144 of the collar 143 by the through holes 145 provided in the collars 143, so that each of the collars 143 fixed to the closed container 12.
Thus, welding can be reliably performed without opening holes due to air blowing in the welded portions 147 of the refrigerant introduction pipes 92 and 94 and the refrigerant discharge pipes 96 and 98. A mounting pedestal 110 is provided on the outer bottom surface of the sealed container 12.

Next, an outline of the operation of the above embodiment will be described. The two-stage compression type compressor 10 is used as, for example, a hot water supply device 150. That is, the hot water supply device 150 includes a heat source unit 151 and a hot water tank unit 156. The heat source unit 151 is connected to the refrigerant at the inlet side of the heat exchanger 152 for water heating from the refrigerant discharge pipe 96 at the outlet side of the two-stage compression type compressor 10. The pipe 153 connected to the pipe 106 and located on the outlet side of the heat exchanger 152 for heating water is connected to the expansion valve 15.
4. The evaporator 155 is connected, and the refrigerant pipe 100 on the outlet side of the evaporator 155 is connected to the refrigerant introduction pipe 92 of the two-stage compression type compressor 10 (FIG. 28).

In the hot water tank unit 156, a water pipe 157 provided in a general household is connected to one side of a hot water storage tank 158 for temporarily storing hot water.
Is branched before being connected to the hot water storage tank 158, and is sequentially connected to the pump 159, the solenoid valve 160, and the pipe 161. The pipe 161 exits the hot water tank unit 156, passes through the heat exchanger 152 for water heating in the heat source unit 151, and is connected to the outlet pipe 162. The outlet pipe 162 exits the heat source unit 151 and returns to the hot water tank unit 15 again.
6 and is connected to the hot water storage tank 158 by piping.
The outlet pipe 162 that has entered the hot water tank unit 156 exits the hot water tank unit 156, and is connected to a faucet in a kitchen or a lavatory or a shower (not shown).

The operation of the two-stage compression type compressor 10 is as follows. First, when the coil 28 of the electric element 14 is energized through the terminal 20 and the wiring (not shown),
4 starts and the rotor 24 rotates. By this rotation, the upper and lower rollers 46 and 48 fitted to the upper and lower eccentric portions 42 and 44 provided integrally with the rotating shaft 16 eccentrically rotate inside the upper and lower cylinders 38 and 40.

As a result, the refrigerant flows through the refrigerant introduction pipe 94 and the suction passage 60 formed in the lower support member 56, as shown in FIG.
0, the low-pressure refrigerant gas sucked into the low-pressure chamber side 40A of the cylinder 40 from the suction port 116
The pressure is compressed to an intermediate pressure by the operation of the vane 52 and the vane 52, and the pressure becomes an intermediate pressure. Refrigerant pipe 1
02. A part of the refrigerant gas discharged into the discharge muffling chamber 64 flows through the communication passage 63 into the electric element 14 side of the upper cover 66 in the closed container 12, and the closed container 12
The inside of the electric element 14 and the discharge muffling chamber 64 have the same intermediate pressure.

Then, from the refrigerant pipe 102 to the refrigerant introduction pipe 9
The intermediate-pressure refrigerant gas sucked into the low-pressure chamber side 38A of the cylinder 38 from the suction port 112 via the suction passage 58 formed in the second support member 54 and the upper support member 54 is supplied to the second stage by the operation of the roller 46 and the vane 50. Is compressed into a high-temperature and high-pressure refrigerant gas, which is heated from the high-pressure chamber side 38B through the discharge port 114, through the discharge muffling chamber 62 formed in the upper support member 54, the refrigerant discharge pipe 98, and the refrigerant pipe 106. Into the heat exchanger 152. Therefore, the high-temperature and high-pressure refrigerant gas radiates heat and exhibits a heat exchange effect with water flowing through the pipe 161, and is then throttled by the expansion valve 154 and further cooled (heat radiated) by the evaporator 155 to be discharged from the refrigerant introduction pipe 94. 1
Is repeated in the compression element 32.

The water in the pipe 161 heated by the heat exchange action in the water heating heat exchanger 152 is supplied to the electromagnetic valve 16.
0 opens, the pump 159 circulates in the hot water storage tank 158 by the operation of the two-stage compression type compressor 10 and
The water in 8 is warmed to a predetermined temperature. Hot water storage tank 158
When the water inside is heated to a predetermined temperature, the solenoid valve 160 is closed and the pump 159 and the two-stage compression type compressor 10 are stopped. Then, when the hot water in the hot water storage tank 158 is used in a kitchen, a washroom, a shower, or the like, the used amount of water is automatically refilled into the hot water storage tank 158 from a water pipe. At this time, since the electromagnetic valve 160 is closed, the hot water in the hot water storage tank 158 is pushed out by the water flowing from the water supply pipe. When the temperature of the hot water storage tank 158 becomes lower than a predetermined temperature, the solenoid valve 160 is opened, the pump 159 and the two-stage compression type compressor 10 are operated, and the heat exchanger 152 for water heating is operated.
The water in the hot water storage tank 158 is heated to a predetermined temperature by the heat exchange action of

Then, by the rotation of the rotating shaft 16, the lubricating oil stored at the bottom of the closed container 12 is removed from the rotating shaft 1.
6 rises in a vertical oil hole 80 formed at the center of the shaft, and flows out of horizontal oil supply holes 82, 84 provided in the middle thereof to the bearings 54A, 56A of the rotating shaft 16 and the vertical eccentric portions 42, 44. Supplied. As a result, the rotation shaft 16 and the upper and lower eccentric portions 42 and 44 can smoothly rotate.

As described above, the discharge port 39 of the second compression element 34, which sucks the refrigerant gas compressed and discharged by the first compression element 32 into the second compression element 34, compresses and discharges the compressed refrigerant gas, is provided. Since the discharge volume 41 of the first compression element 32 is smaller than the discharge port 41 of the first compression element 32, the displacement volume of the second compression element 34 is set to 55% or more and 85% or less of the displacement volume of the first compression element 32. The first compression element 3 is applied to the refrigerant gas discharged from the discharge port 39 of the second compression element 34.
2 increases the volumetric flow rate of the refrigerant gas discharged from the discharge port 41 of the first compression element 3.
2 can be suppressed from increasing, and at the same time, the dead volume of the second compression element 34 can be reduced.

Particularly, since the diameter of the discharge port 39 of the second compression element 34 having a high pressure is made smaller than the diameter of the discharge port 41 of the first compression element 32 having a low pressure, the pressure loss of the first compression element 32 is reduced. Can be done. Thereby, the performance of the two-stage compression type compressor 10 can be maximized. Also, by reducing the pressure loss, it is possible to make the compression balance between the first compression element 32 and the second compression element 34 uniform. Therefore, the vibration due to the torque fluctuation of the two-stage compression type compressor 10 can be effectively reduced, and the efficiency can be greatly improved.

In each of the embodiments, the two-cylinder two-stage compression type compressor 10 in which the rotary shaft 16 is vertically mounted has been described. Needless to say, it can also be applied to.

Further, the multi-stage compression type compressor has been described as a two-stage compression type compressor having first and second compression elements. However, the present invention is not limited to this, and three-stage, four-stage or more compression elements may be provided. It can be applied to a multi-stage compression compressor.

Although the two-stage compression type compressor 10 is used as the hot water supply device 150, the invention is not limited to this, and the present invention is also effective when used for heating a room.

In the above embodiment, the vane 50 is supported on the cylinder 38 so as to be able to advance and retreat, and a back pressure is applied to bring the tip end of the vane 50 into contact with the outer peripheral surface of the roller. Although the description has been given of the case where the compression is performed, the present invention is not limited to this. Note that only one compression element 170 is shown. The compression element 170 has a vane 171 integrally provided on a part of the outer periphery of the roller 172 so as to protrude toward the outer diameter direction of the roller 172, and a cylinder 17.
A circular holding hole 176 such as a cylinder or a sphere is provided in the suction port 174 in the middle of the suction port 174 and the discharge port 175, and a receiving groove 178A having one end opened to the cylinder chamber 177 side is formed in the holding hole 176. The holding member 178 is rotatably held, and the tip of the protruding side of the vane 171 is slidably inserted into the receiving groove 178A of the supporting member 178.
The roller 172 is configured to be non-rotating so as not to co-rotate with the crankshaft as a drive shaft, and the roller 172 is revolved in the cylinder 173 by driving the rotary shaft 179. When the vane 171 is provided on a part of the outer periphery of the rotor, a mounting groove is formed on the roller 172 side so that a part of the base end of the vane 171 can be inserted, and the base part of the vane 171 is inserted into the mounting groove. It is inserted and integrated with an adhesive or integrated by brazing.

[0058]

As described above in detail, according to the present invention, a motor-driven element and first and second compression elements driven by the motor-driven element are provided in a closed container, and the first compression element compresses the power. And
Since the discharged refrigerant gas is sucked into the second compression element, compressed, and discharged, the discharge port of the second compression element is smaller than the discharge port of the first compression element. For example, by setting the rejection volume of the second compression element to 55% or more and 85% or less of the rejection volume of the first compression element as described in claim 2, discharge is performed from the discharge port of the second compression element. It is possible to suppress an increase in pressure loss of the first compression element despite an increase in the amount of refrigerant gas discharged from the discharge port of the first compression element with respect to the refrigerant gas. At the same time, it is possible to reduce the dead volume of the second compression element. Therefore, the pressure loss of the first compression element can be greatly reduced, and high volume efficiency can be realized.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional side view of a two-stage compression type compressor having first and second compression elements as an embodiment of the multi-stage compression type compressor of the present invention.

FIG. 2 is a plan view of the two-stage compression compressor of FIG.

FIG. 3 is a plan view of an upper cover.

FIG. 4 is a view of the upper cover of FIG.

FIG. 5 is a plan view of an upper support member.

FIG. 6 is an enlarged view showing the vicinity of a discharge port of the upper support member of FIG.

7 is a vertical sectional side view showing the vicinity of a discharge port of the upper support member of FIG. 5;

FIG. 8 is a plan view of a lower support member.

FIG. 9 is an enlarged view showing the vicinity of a discharge port of the lower support member of FIG. 8;

FIG. 10 is a vertical sectional side view showing the vicinity of a discharge port of the lower support member of FIG. 8;

FIG. 11 is an enlarged view of the upper and lower support members showing a state in which the valve body is attached.

FIG. 12 is a vertical sectional side view of an upper support member.

FIG. 13 is a rear view of the upper support member of FIG.

FIG. 14 is a vertical sectional side view of a lower support member.

FIG. 15 is a rear view of the lower support member of FIG. 14;

FIG. 16 is a rear view of the cylinder on the high pressure side.

FIG. 17 is a view of the high-pressure side cylinder of FIG. 16 taken along line BB.

FIG. 18 is a view showing a state in which a spring is attached to a storage section provided in the high pressure side cylinder of FIG.

FIG. 19 is a view showing a state in which a spring is attached to a spring hole provided in a cylinder on a low pressure side.

FIG. 20 is an illustrative view explaining a configuration of each compression unit in FIG. 1;

FIG. 21 is a plan view showing an embodiment of a rotating shaft including a vertical eccentric portion in FIG. 1;

FIG. 22 is a view taken along line CC of FIG. 21;

FIG. 23 is an enlarged vertical sectional side view of a collar portion of each refrigerant introduction pipe attached to the container body.

FIG. 24 is a front view of the sleeve.

FIG. 25 is a front view of the sleeve of FIG. 24;

FIG. 26 is a front view of a tube.

FIG. 27 is a front view of a collar.

FIG. 28 is a circuit diagram of a hot water supply apparatus to which the multi-stage compression compressor of the present invention is applied.

FIG. 29 is a schematic plan view showing a western configuration of a compression element of an internal intermediate pressure type two-stage compression type rotary compressor according to another embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Two-stage compression type compressor 12 Hermetic container 14 Electric element 16 Rotary shaft 18 Rotary compression mechanism 32 First compression element 34 Second compression element 36 Intermediate partition plate 38 Cylinder 38A Low pressure chamber side 38B High pressure chamber side 39 Discharge port 40 Cylinder 40A Low pressure chamber side 40B High pressure chamber side 41 Discharge port 54 Upper support member 56 Lower support member 62 Discharge muffler chamber 64 Discharge muffler chamber 66 Upper cover 68 Lower cover 150 Hot water supply unit 151 Heat source unit 152 Heat exchanger for water heating 156 Hot water tank unit 157 Water pipe 158 Hot water storage tank 159 Pump

 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Satoru Imai 2-5-5 Keihanhondori, Moriguchi-shi, Osaka Sanyo Electric Co., Ltd. (72) Inventor Masaya Tadano 2-5-2 Keihanhondori, Moriguchi-shi, Osaka No. 5 Sanyo Electric Co., Ltd. (72) Atsushi Oda 2-5-5 Keihanhondori, Moriguchi-shi, Osaka F-term in Sanyo Electric Co., Ltd. 3H029 AA04 AA13 AB03 BB43 CC09 CC23 CC24 CC25 3H076 AA16 BB21 BB43 CC92 CC93 CC94 CC96

Claims (2)

[Claims] 1. An electronic device comprising: an electric element in a closed container; first and second compression elements driven by the electric element;
The refrigerant gas compressed and discharged by the compression element
A multi-stage compression compressor, wherein a suction port of the second compression element is smaller than a discharge port of the first compression element. . 2. The multi-stage compression type compressor according to claim 1, wherein the displacement volume of said second compression element is set to 55% or more and 85% or less of the displacement volume of said first compression element.