JP3574904B2 - Closed displacement compressor - Google Patents

Description

[0001]
[Industrial applications]
The present invention relates to a positive displacement fluid machine, and more particularly to a closed displacement positive displacement compressor suitable for use in a refrigeration and air conditioning cycle such as a refrigerator or an air conditioner.
[0002]
[Prior art]
A first known technology of the conventional rotary positive displacement compressor is a scroll compressor. The principle structure of this type is a type in which a fixed scroll provided with a spiral wrap and an orbiting scroll are engaged with each other to constitute a compression working chamber, as is well known.
[0003]
Conventional scroll compressors have an orbiting scroll slidably engaged with a crankshaft arranged at the center of rotation of an electric motor.SaidBy orbiting by the rotation of the crankshaft, gas flows into the compression working chamber formed by the fixed scroll wrap and the orbiting scroll wrap from the outer peripheral portion, is compressed toward the center, and is provided at the center of the fixed scroll. Discharge port.
[0004]
The scroll compressor is characterized in that gas compression is performed in many compression working chambers at the same time, so that gas leakage between the compression working chambers is small and high efficiency. Further, there is a feature that vibration is small due to small torque fluctuation.
[0005]
As described above, the scroll compressor orbits the orbiting scroll with a constant radius in a state where the fixed scroll and the orbiting scroll are combined, so that the size of the gap is determined by the shape accuracy of the scroll member and the size of the orbiting radius. Is done.
[0006]
However, in order to maintain high performance, it is necessary to reduce the gap in the compression working chamber.
[0007]
As a countermeasure against this, as disclosed in Japanese Patent Application Laid-Open No. 62-282186, for example, there is a technology in which a drive shaft of an orbiting scroll is disposed together with an elastic body in an eccentric drive shaft of a crankshaft. Thereby, the radius of movement of the orbiting scroll can be made variable, and the radial gap of the scroll wrap is kept small by constantly biasing the drive shaft of the orbiting scroll outward.
[0008]
A scroll compressor similar to the above is described in JP-A-2-264181, and the supply of lubricating oil to each sliding portion inside the compressor is performed through an oil supply hole provided in a crank. It was a method.
[0009]
Further, as a second known technique, a cylinder having a cylindrical inner surface and an eccentric motion are performed in the cylinder as disclosed in JP-A-64-104996.rollerThere is a rotary compressor constituted by a vane and the like reciprocating in a cylinder. Rotary compressors use a crankshaft that is driven directly by a motor to revolve the rollers inside the cylinder.The gap between the roller outer peripheral surface and the cylinder inner peripheral surface is a fixed amount determined during assembly. It is a structure that is maintained.
[0010]
A large load is applied to the rotary sliding portion between the crankpin portion of the crankshaft and the roller and the rotary sliding portion of the motor bearing due to the pressure of the compressed gas acting on the outer peripheral surface of the roller. The roller and the vane were separated from each other, and the vane incorporated in the cylinder was configured to press against the outer peripheral surface of the roller by back pressure or spring force to maintain the security.
[0011]
[Problems to be solved by the invention]
In the scroll compressor according to the first known example, the gas force of the compressed gas acting on the orbiting scroll and the centrifugal force of the orbiting scroll act on the engagement portion between the eccentric drive shaft of the crankshaft and the drive shaft of the orbiting scroll. At this time, since the crankshaft rotates, the centrifugal force becomes a rotational load on the shaft. The gas force of the compressed gas is also a rotational load due to the scroll type feature.
[0012]
Therefore, a very large load acts on the elastic body disposed in the eccentric drive shaft of the crankshaft.To overcome this and always press the orbiting scroll outward, the spring force of this elastic body must be relatively strong. Must. As a result, there have been problems that assemblability when assembling the orbiting scroll and the crankshaft is reduced, and that the structure is complicated.
[0013]
Further, in the conventional technology, the point of action of the force for orbiting the orbiting scroll and the compressed gas force acting on the orbiting scroll wrap are determined.Based onDue to the difference in the point of action of the radial force, there is a problem that an overturning moment is generated in the orbiting scroll and the stable motion of the orbiting scroll is easily damaged.
[0014]
When the unstable motion of the orbiting scroll occurs, the moment load simultaneously acts on the bearing of the eccentric drive shaft of the crankshaft, and thus has a problem that the reliability of the elastic body is affected.
[0015]
Since a relatively large radial load is applied to a rotating sliding portion having a high sliding speed, such as a bearing portion of an eccentric shaft of a crankshaft, mechanical friction loss increases, causing a decrease in compressor efficiency. . Under severe operating conditions, sliding conditions become severe, and there is a problem that wear and seizure occur in the bearing portion, thereby reducing the reliability of the compressor.
[0016]
Further, a problem with the rotary compressor of the second known example is that the minimum gap between the cylinder and the roller is determined by the precision of parts such as the cylinder, the roller, and the crankshaft.
[0017]
That is, since the roller is driven by the crankshaft having a fixed radius, the size of the gap is already given by the assembled state. Since the leading end of the vane and the outer peripheral portion of the roller are always slid with a large force applied thereto, the outer peripheral portion of the roller wears as the operation time elapses.
[0018]
As a result, since the roller diameter is reduced, the minimum clearance between the roller and the cylinder is also increased, and there is a problem that during the operation of the compressor, the leakage of the compressed gas increases and the performance of the compressor is reduced.
[0019]
Further, in a compressor for a refrigerating air conditioner, a phenomenon may occur in which a liquid is mixed into a suction gas. At this time, a very large load may be generated due to the compression of the liquid.
[0020]
In the second known example, a countermeasure at the time of liquid compression is not sufficiently considered, and if a liquid compression phenomenon occurs during operation, there is a possibility that the shaft, bearings, moving parts, etc. may be seriously damaged. Was.
[0021]
A first object of the present invention is to provide a closed displacement type compressor having a function of adjusting a gap between a fixed member forming a compression chamber and a revolving member in order to reduce leakage of compressed gas from a compression working chamber. That is.
[0022]
A second object of the present invention is to avoid an abnormal increase in pressure in the compression working chamber by increasing the radial direction of the gap between the fixed member and the turning member when liquid is mixed into the compression working chamber and liquid compression occurs. It is an object of the present invention to provide a hermetic positive displacement compressor having the function of
[0023]
Of the present inventionA third object is to provide a lubrication system suitable for a hermetic positive displacement compressor having the function of adjusting the gap as described above and a hermetic positive displacement compressor having a function of avoiding abnormal pressure. .
[0024]
[Means for Solving the Problems]
The enclosed positive displacement compressor of the present invention basically includes a rotor that replaces a conventional crankshaft as a transmission mechanism that converts the rotation of an electric motor into orbital motion of a rotor such as an orbiting scroll or a roller.OrThe lever member is inclined with respect to the rotation axis of the electric motor.
[0025]
That is, the closed displacement type compressor of the present invention includes a compression mechanism having a pair of fixed members forming a compression working chamber and a rotating rotor member in a closed vessel, and a rotating center of the rotating rotor driven by the compression mechanism. A motor with a rotating shaft coaxial with the shaft is installed, and as a transmission mechanism that transmits the driving force of the motor to the compression mechanism, the tip is eccentric from the rotating shaft of the motor by the turning radius and connected to the turning rotor member by a spherical pair. The intermediate portion is supported with a spherical pair at a fixed point on the rotation axis of the motor, and the rear end is on an extension of a straight line connecting the fixed point with the spherical pair center point at the front end at the rotor portion of the motor. In this embodiment, a lever member is provided which is connected to a spherical pair at the position, and a tilt angle adjusting mechanism for changing the tilt angle of the lever member with respect to the rotation axis of the electric motor and a turning radius adjusting mechanism are provided.
[0026]
In order to achieve the first object, the sealed positive displacement compressor of the present invention has a closed container when the compressor is a scroll type compressor.Inside the compression working chamberA compressor having a pair of fixed scrolls and orbiting scrolls, and a motor having a rotating shaft arranged coaxially with the orbiting center axis of the orbiting scrolls. The first spherical bearing formed at the front end and the first spherical bearing provided at a position eccentric by the turning radius from the turning center axis at the orbiting scroll portion at the front end portion, and the first spherical bearing formed at the intermediate portion. The two spherical portions and the second spherical bearing provided at a fixed point on the rotating shaft of the motor are spherically paired, and the first and second portions of the spherical bush and the rotor of the motor are slidably fitted on the round shaft portion formed at the rear end. A third spherical bearing provided at a position on an extension of a straight line connecting the centers of the second spherical portions is paired with a spherical surface, a lever member inclined with respect to the rotation axis of the electric motor is provided, and the rotor of the electric motor is connected to the rotation axis. Move in direction A positioning mechanism for positioning by a supporting mechanism for supporting the second spherical bearingWas provided.Here, this scroll-type compressor is referred to as a first hermetic-type positive displacement compressor of the present invention.
[0027]
In order to achieve the second object, the sealed positive displacement compressor of the present invention (referred to as a second sealed positive displacement compressor) is a first sealed positive displacement compressor, in which a rotor of an electric motor includes: Third spherical bearingSaidAn elastic member is provided for pressing the rotor radially outward. In this case, the lever member is preferably such that the distance from the second spherical portion at the intermediate portion to the spherical bush attached to the rear end portion is larger than the distance from the second spherical portion to the first spherical portion at the front end portion. Good.
[0028]
In the first and second sealed positive displacement compressors, the rotor of the electric motor includes a hollow cylindrical main rotor member, a disk integrally attached to a rear end side of the main rotor member, and a rear end from the center of the disk. And a sub-rotor member having a shaft portion protruding from the main rotor member, and a third spherical bearing is preferably disposed in a disk of the sub-rotor member.
[0029]
The main rotor member of the electric motor may have a slanted hole in which the lever member is disposed, and may be close to a solid.
[0030]
In order to achieve the third object, the hermetic positive displacement compressor of the present invention has the following lubrication oil supply system (referred to as a first lubrication oil supply system). That is, in the first and second hermetic type positive displacement compressors, the oil supply hole communicating from the shaft end to the third spherical bearing in the auxiliary rotor member is provided in the third spherical bearing.SaidAn oil supply hole penetrating the bearing is provided, and an oil supply hole communicating with the first spherical bearing, the second spherical bearing, and the spherical bush is provided in the shaft of the lever member, the oil supply holes communicate with each other, and the shaft end of the sub rotor member is provided. And the lubricating oil stored in the sealed containerCommunicated.
[0031]
Then, at least one of a contact surface between the first spherical portion and the first spherical bearing, at least one of a contact surface between the second spherical portion and the second spherical bearing, and at least one of a contact surface between the round shaft portion and the spherical bush. It is preferable to provide a lubrication groove in the groove.
[0032]
A helical member having a flow path helically twisted in the longitudinal direction may be attached to an oil supply hole provided in the shaft portion of the sub rotor member.
[0033]
Another lubricating lubricating system (second lubricating lubricating system) that replaces the first lubricating lubricating system has a piston member in contact with the outer circumferential surface of the orbiting scroll in the first hermetic positive displacement compressor. A pump mechanism for sucking up the lubricating oil stored in the bottom of the sealed container is provided by a pumping action of the reciprocating motion of the piston member accompanying the orbiting motion of the orbiting scroll member.SaidA lubrication hole is provided from the pump mechanism to a hole for accommodating the first spherical bearing, and a lubrication hole communicating with the first spherical bearing, the second spherical bearing, and the spherical bush at the front end to the rear end is provided in the lever member shaft.Provided.
[0034]
In this system, the first spherical bearing andSaidIt is preferable to provide a seal member between the first spherical bearing and a hole for accommodating the first spherical bearing.
[0035]
Again, in order to achieve the first object, the sealed positive displacement compressor of the present invention has a closed container when it is a rotary type compressor.Fixed inAn electric motor having a compression mechanism including a cylinder, rollers rotating in the cylinder, and vanes forming a compression working chamber by partitioning a space between the cylinder and the rollers, and a rotating shaft arranged coaxially with the rotation center axis of the rollers. And a positioning mechanism and a support mechanism using a lever member employed in the first hermetic positive displacement compressor as a transmission mechanism for transmitting the driving force of the electric motor to the compression mechanism. This rotary-type compressor is referred to as a third hermetic positive displacement compressor of the present invention.
[0036]
In order to achieve the second object, a sealed positive displacement compressor (referred to as a fourth closed positive displacement compressor) of the present invention is a third closed positive displacement compressor, wherein a rotor of an electric motor is: Third spherical bearingSaidAn elastic member that presses radially outward of the rotorProvided.
[0037]
The lever member preferably has a distance from the second spherical portion at the intermediate portion to the spherical bush attached to the rear end portion greater than the distance from the second spherical portion to the first spherical portion at the front end portion.
[0038]
In the third and fourth sealed positive displacement compressors, the rotor of the electric motor includes a hollow cylindrical main rotor member and a sub rotor member integrally attached to a rear end side of the main rotor member, and levers are provided. Preferably, the member is disposed through the main rotor member and the third spherical bearing is disposed within the sub-rotor member.
[0039]
[Action]
The operation of the scroll type compressor, which is the first and second closed type positive displacement compressors of the present invention, will be described as a representative of the positive displacement type compressor of the present invention.
[0040]
The lever member is supported by a spherical pair (this center point is referred to as a fulcrum) at a fixed point on the rotating shaft of the motor at an intermediate portion thereof, and the front end of the lever member is eccentric from the rotating shaft of the motor by the turning radius of the orbiting scroll. The orbiting scroll is connected to the spherical pair (the center is called the load point) to incline the lever member with respect to the rotation axis of the electric motor. The rear end of the lever member corresponds to the tilt angle of the lever member at the sub-rotor. Because it is connected to the sub-rotor member by a spherical pair (the center point is called a power point) at an eccentric position by the distance, when the motor rotates, the lever member draws two cones whose vertexes abut each other. And the driving force of the electric motor is transmitted from the spherical pair of the auxiliary rotor member (point of force) to the spherical pair of the orbiting scroll (load point) via the lever member, and the orbiting scroll orbits relative to the fixed scroll. .
[0041]
In this way,Gas is compressed in a compression working chamber formed between the fixed scroll and the orbiting scroll.
In addition, by providing a hole into which the member is inserted in the main rotor member of the electric motor and making the member solid rather than hollow, a decrease in magnetic permeability in an electromagnetic field can be minimized.
[0042]
Next, the function of adjusting the radial gap between the pair of fixed scrolls and the orbiting scroll forming the compression working chamber will be described.
[0043]
When the rotor of the electric motor is moved, for example, in the orbiting scroll direction by the positioning mechanism, the spherical bush constituting the spherical pair at the rear end of the lever member is slip-fitted.Lever memberAnd the eccentric distance of the third spherical bearing with respect to the electric motor rotating shaft is constant and does not change, so that the tilt angle of the lever member increases, and the gap between the fixed scroll and the orbiting scroll decreases.
[0044]
According to this function, at the time of assembling the compressor, the tilt angle of the lever member can be arbitrarily adjusted by moving the rotor of the electric motor in the direction of the rotation axis thereof by the positioning mechanism. Adjusting this angle of inclination, without being affected by the accuracy, reduces the radial gap between the contact points that make up the compression working chamber.Can be smaller.
[0045]
The function of the elastic member of the scroll type compressor, which is the second hermetic positive displacement compressor, that is, the function of the elastic member for pressing the third spherical bearing paired with the spherical bush attached to the rear end of the lever member will be described. I do.
[0046]
If liquid compression occurs during operation of the compressor, excessive pressure will be generated in the compression working chamber. At this time, the force due to the excessive pressure is transmitted from the lever member to the elastic member via the spherical bush and the third spherical bearing, and the force overcomes the elastic force of the elastic member, and the inclination angle of the lever member decreases.
[0047]
Therefore, the gap in the compression working chamber becomes large, high-pressure liquid leaks, and the pressure in the compression working chamber decreases.
The elastic member is restored and the inclination angle of the lever member is increased, so that an appropriate gap is automatically maintained.
[0048]
Then, by increasing the distance from this fulcrum to the fulcrum at the rear end of the lever member compared to the distance from the load point at the front end of the lever member to the fulcrum at the middle part of the lever member, the leverage of the leverage The load on the power point at the rear end of the member can be reduced, the load on the spherical bush and the third spherical bearing at the power point can be reduced,small I can do it.
[0049]
The value of the sliding speed at the load point is significantly smaller because the sliding speed is a swinging motion as compared with the conventional rotation of the crankshaft.
[0050]
Since the elastic member disposed in the rotating member generates a force for pressing the lever member outward, the lever member is maintained to have a large inclination angle.
[0051]
During rotation, a centrifugal force acts on the lever member inclined with respect to the rotation axis of the electric motor, so that the inclination angle is kept large.
[0052]
As a result, the spherical and even support points of the rotor located on the opposite side of the fulcrum position also move radially outward, and conversely, the orbiting scroll has a larger orbital radius, and the gap at the contact point with the fixed scroll becomes larger. Keep small.
[0053]
The first lubrication and lubrication system will be described.
[0054]
Under the operating condition of the compressor, the high pressure due to the discharge gas acts on the lubricating oil at the bottom of the compressor, but the pressure in the space in front of the compression mechanism in the closed container is larger than the suction pressure and higher than the discharge pressure. By setting the intermediate pressure to a small value, the lubricating oil is supplied to each sliding portion around the lever member through an oil supply hole in the member communicating therewith due to the pressure difference and the centrifugal force of each rotating member.
[0055]
More specifically, the lubricating oil at the bottom of the compressor flows into the auxiliary rotor member from the shaft end to the oil supply hole communicating with the third spherical bearing, passes through the oil supply hole penetrating through the third spherical bearing, and enters the lever member shaft. The oil is supplied from the formed oil supply hole through an oil supply hole communicating with the first spherical bearing and the second spherical bearing.
[0056]
And the shaft side forming the spherical pair and the rotating pair of the lever memberOrSince at least one of the bearings is provided with an oil supply groove in the circumferential direction, a sufficient and sufficient amount of lubricating oil is supplied to the sliding surfaces of each pair.
[0057]
By the way, the spiral member provided in the oil supply hole of the sub-rotor member in contact with the lubricating oil at the bottom of the compressor rotates during the operation of the compressor and assists in pumping the lubricating oil.
[0058]
The second lubrication oil supply system will be described. In the first hermetic-type positive displacement compressor, the pump mechanism provided on the outer circumferential surface of the orbiting scroll performs a reciprocating motion of the piston member with the orbiting motion of the orbiting scroll member to perform a pump action.
[0059]
As a result, the lubricating oil sucked up from the bottom of the sealed container flows into the hole for accommodating the first spherical bearing from the oil supply hole formed in the orbiting scroll member, and is formed in the axial direction of the lever member from the front end surface of the lever member. The lubrication is performed by reaching the first spherical bearing, the second spherical bearing, and the spherical bush through the lubrication hole, and through the lubrication hole branched from the lubrication hole. The seal member provided between the first spherical bearing and the hole for accommodating the first spherical bearing is provided so that a large amount of lubricating oil flows into the oil supply hole of the lever member. This pump mechanism is especiallyscrollEffective for lubrication of compressors.
[0060]
As a result, in the drive mechanism for imparting the revolving motion to the orbiting scroll, since the round shaft and the spherical bush, and the spherical bush and the third spherical bearing at the rear end of the lever member slide and rotate, the sliding speed is high. The dynamic load is reduced, while the second spherical portion and the second spherical bearing (fulcrum) at the intermediate portion of the lever member, and the first spherical portion at the front end of the lever member and the first spherical bearing (the load point) in the orbiting scroll are reduced. In ()), the sliding load is large, but the sliding speed is a small swinging motion. Therefore, the sum of the mechanical friction loss due to the radial load in those sliding portions is small, and there is no sliding portion where the sliding conditions are particularly severe. Thereby, the efficiency and reliability of the compressor can be improved. In addition, the degree of freedom in selecting a sliding material is increased.
[0061]
The operation of the scroll type compressor, which is the first and second closed displacement type compressors of the present invention, has been described above.
[0062]
Among them, the function of adjusting the gap between the rotating member and the fixed member forming the compression working chamber, and the function of the elastic member that prevents excessive pressure in the compression working chamber when liquid compression occurs, are the third and third aspects of the present invention. It is also provided in a rotary type compressor, which is a four hermetic type positive displacement compressor.
[0063]
If the fixed scroll is replaced with a cylinder and the orbiting scroll is replaced with a roller, the operation of both functions will be the same as above,Related to rotary type compressorsDescription is omitted.
[0064]
【Example】
Next, an embodiment of the hermetic positive displacement compressor according to the present invention will be described with reference to FIGS.
[0065]
Embodiment 1
FIG.Embodiment 1 of the present inventionFIG. 2 is a vertical cross-sectional view showing the overall configuration of a hermetic scroll compressor vertically mounted on a hermetic positive displacement compressor, and FIG. 2 is a diagram showing engagement of scroll members in the AA cross-sectional view of FIG.
[0066]
This compressor generally includes a compression mechanism unit having a combination of a fixed scroll 1 and a orbiting scroll 2 that rotates (orbits) eccentrically with respect to the axis of the fixed scroll 1, and a compression mechanism that applies a driving force to the orbiting scroll 2. A motor 7 which is an electric motor for driving the machine, a lever member 6 for connecting the motor 7 and the orbiting scroll 2 to transmit a driving force, a bearing portion of a rotor of the motor 7, and the above-described compression in order from an upper portion to a lower portion. A cylindrical hermetic container 9 that houses the mechanism, the motor 7, and the bearing of the rotor of the motor 7 and stores the bearing at the bottom, the joint between the lever 6, the orbiting scroll 2, and the motor 7, and the support of the lever 6. Lubrication system for lubricating pointsAnd fromIt is configured.
[0067]
Axis of fixed scroll 1That is,The turning center axis of the orbiting scroll 2 and the support point of the lever member 6 are located on the rotation axis of the motor 7 (abbreviated as the motor axis).
[0068]
The fixed scroll 1 that constitutes the compression mechanism section includes a head plate 1b and a spiral scroll wrap 1a that protrudes from one surface of the head plate 1b. The orbiting scroll 2 includes a head plate 2b, And a spiral scroll wrap portion 2a protruding from one surface of the end plate portion 2b. Each of the scroll wrap portions (hereinafter simply referred to as wrap portions) 1a and 2a of the fixed scroll 1 and the orbiting scroll 2 is formed by an involute curve or the like.
[0069]
As shown in FIG. 2, the fixed scroll 1 and the orbiting scroll 2 are engaged with each other by engaging the respective wrap portions 1a, 2a to form a compression working chamber 10 between the two wrap portions 1a, 2a.
[0070]
The fixed scroll 1 and the orbiting scroll 2 are vertically combined, and the outer periphery of the fixed scroll 1 is fixedly supported by the frame 3 from below, and the orbiting scroll 2 is slidably supported by the frame 3 from below.
[0071]
Further, a boss protrudes from the lower surface of the end plate portion 2b of the orbiting scroll 2 at a position eccentric from the axis of the motor, and a joint portion between the orbiting scroll 2 and the lever member 6 is disposed in the boss.
[0072]
The outer periphery of the frame 3 is fixed to the closed container 9 by welding or the like. An Oldham ring 4 that prevents rotation when the orbiting scroll 2 is turned is provided on the lower surface of the end plate portion 2b.
[0073]
The end plate portion 1b of the fixed scroll 1 is provided with a suction port 5 and a discharge port 12 at the center thereof, and is fixed to the frame 3 by bolts 14a at an outer peripheral portion.
[0074]
A current introduction terminal 21, a suction pipe 11, and a discharge pipe 13 are provided in the closed container 9. The suction pipe 11 is fixed to the outer peripheral portion of the end plate 1 b of the fixed scroll 1 and communicates with the suction port 5.
[0075]
In the motor 7, a stator 7b of the motor 7 is fixed to the closed casing 9, and a hollow cylindrical main rotor member 7a whose outer periphery is surrounded by a permanent magnet 7c is aligned with the axis of the compressor as a rotor element of the motor 7. And are arranged.
[0076]
The shaft portion 22 formed at the center of the upper end of the main rotor member 7a is rotatably supported by being fitted into a hole of a boss of the upper frame 3. At the lower end of the main rotor member 7a, a sub-rotor member 20 generally including a disk and a shaft portion 25 extending downward from the disk along the axis of the motor 7 is integrated with the main rotor member 7a by bolts 14b. Attached.
[0077]
A hole is formed in the sub rotor member 20 on the side facing the internal space 42 of the main rotor member 7a at a position eccentric from the motor axis, and a joint between the lever member 6 and the motor 7 is formed in the hole. Are arranged.
[0078]
The shaft portion 25 of the sub-rotor member 20 is supported by a radial bearing and a thrust bearing. The radial bearing and the thrust bearing are formed at the center of an auxiliary bearing support plate 24 fixed radially in the closed casing 9. The boss portion 30 is disposed in the hole. The radial bearing is composed of a spherical bush 16 slidingly fitted on the shaft portion 25 and a lower spherical bearing 17 for supporting the bush. The thrust bearing is composed of a spherical body 27 in contact with the lower end surface of the shaft portion 25 and a thrust plate for supporting the same. 26.
[0079]
The thrust plate 26 is positioned by a ring screw 28 screwed into the hole of the boss 30 of the auxiliary bearing support plate 24 from below.
[0080]
The lever member 6 has a joint part with the orbiting scroll 2 at the upper end, a joint part with the motor 7 at the lower end, and has a bearing part serving as a support point in the middle between the upper and lower parts.
[0081]
The support point of the lever member 6 is a fixed point on the motor axis, and the joint (load point) between the lever member 6 and the orbiting scroll 2 is separated from the motor axis by the turning radius of the orbiting scroll 2. .
[0082]
Accordingly, the axis of the lever member 6 is inclined with respect to the motor axis by the angle θ corresponding to the turning radius, and the joint (power point) between the lever member 6 and the motor 7 is formed on the sub rotor member 20 at the angle θ. At a position eccentric from the motor shaft center by an amount corresponding to
[0083]
The inclined lever member 6 is provided so as to penetrate the space 42 in the main rotor member 7 a, and a spherical portion 6 c (second spherical portion) serving as a support point is formed in the middle between the inclined lever member 6 and the spherical portion 6 c and the frame 3. A spherical pair is formed from the main bearing 15 (second spherical bearing) provided in the hole of the boss, and a spherical portion 6a (first spherical portion) is formed at the upper end of the lever member 6, and the lever 6 rotates with the spherical portion 6a. The turning bearing 18 (first spherical bearing) provided in the hole of the boss at the lower part of the scroll 2 forms a spherical pair as a load point, and the lower end of the lever member 6 is a spherical surface which is slidingly fitted on the cylindrical shaft. The bush 16 and the lower spherical bearing 17 (third spherical bearing) provided in the hole of the sub-rotor member 20 form a spherical pair which is a point of power.
[0084]
At the lower end of the lever member 6, the outer peripheral surface of the lever member 6 and the inner peripheral surface of the spherical bush 16 are rotatably fitted together, and the spherical bush 16 and the lower spherical bearing 17 have a spherical pair structure. The lower spherical bearing 17 is further supported by an elastic member 19.
[0085]
FIG. 3 shows a configuration in which the elastic member 19 is formed as an integrated product having elasticity, and is disposed on the center side of the lever member 6. FIG. 4 shows a structure in which the elastic member 19 is formed of a leaf spring-shaped member and is disposed on the center side. Therefore, the lower end of the lever member 6 is pressed outward in the radial direction. For this reason, even the pivot bearing 18 at the upper end of the lever member 6 is pressed further outward.
[0086]
As a result, in the contact portion forming the compression working chamber 10, the orbiting scroll 2 is always pressed against the fixed scroll 1, and the gap between the respective scroll wrap portions 1a, 2a is kept small.
[0087]
The main rotor member 7a is supported by the slide bearing 23 via the sub-rotor member 20 and has a gap at the upper end, so that the main rotor member 7a can move in the gap in the axial direction. Further, when the main rotor member 7a is moved in the axial direction, the inclination angle of the lever member 6 changes, and the displacement amount of the orbiting scroll 2 also changes.
[0088]
Therefore, when the position of the ring screw 28 is changed, the inclination angle of the lever member 6 changes. Since the tilt angle of the lever member 6 is small, the radial displacement of the orbiting scroll 2 becomes very small with respect to the axial displacement of the ring screw 28, and the positioning of the orbiting scroll 2 can be finely adjusted by the ring screw 28.
[0089]
As a result, the ring screw 28 can absorb the machining error and the assembly error with respect to the meshing portion of the scroll wrap portions 1a and 2a, and can provide the minimum clearance of the contact portion of the compression working chamber 10. In this state, the position of the ring screw 28 is fixed by tightening the lock nut 29, so that the sealing state of the compression working chamber 10 is suitably adjusted.Can be maintained.
[0090]
When the motor 7 rotates, the lever member 6 rotates while drawing a conical trajectory with the main bearing 15 as a support point.
The load point at the upper end of the lever member 6 revolves at a radius suitable for the orbiting scroll 2 to orbit.
[0091]
As a result, the orbiting scroll 2 orbits with respect to the fixed scroll 1, and gas flows into the compression working chamber 10 from the suction pipe 11. The gas is compressed to a predetermined pressure in the compression operation chamber 10 and the like, and is discharged into a space in the closed container 9 from a discharge port 12 provided in the center of the fixed scroll 1.
The gas that has been compressed to a high pressure temporarily stays in this space and is then discharged out of the machine through the discharge pipe 13.
[0092]
On the other hand, the lubricating oil 8 is pumped up from the lower part of the closed vessel 9 due to a pressure difference or the like, and is supplied to each bearing through an oil supply hole formed in the sub-rotor member 20 or the lever member 6 to be used for lubrication. It has become.
In the lever member 6, since the frictional force of the main bearing 15 serving as a support point is large and the frictional force of the lower spherical bearing 17 is small, the state where the lever member 6 itself hardly rotates is maintained.
[0093]
As a result, the mechanical friction loss in the bearing of each spherical pair is small, and the compressor can be operated with high efficiency.Can drive.
Further, when a fluid such as a liquefied gas flows from the suction port 11, the pressure in the compression working chamber 10 abnormally increases, and the orbiting scroll 2 tends to separate from the fixed scroll 1. At this time, the load acting on the slewing bearing 18 acts to press the lever member 6 toward the center, but this load is received by the lower spherical bearing 17.
[0094]
As a result, the elastic member 19 is deformed, the inclination angle of the lever member 6 is reduced, and the orbiting scroll 2 is separated from the fixed scroll 1. When the high pressure gas leaks into the low pressure side compression working chamber 10 and becomes low pressure, the elastic force of the elastic member 19 prevails, the inclination angle of the lever member 6 returns to a predetermined angle, and the normal compression operation is continued. .
[0095]
In this way, an abnormal increase in pressureCan be avoided,Prevent damage to the scroll wraps 1a and 2aCan be prevented.
The load acting on the lower spherical bearing 17 is such that the distance from the support point to the load point is considerably smaller than the distance from the support point to the power point, so that the elastic force of the elastic member 19 can be reduced from the leverage principle, Ease of assemblyCan be securedAt the same time, high reliability can be secured as a drive mechanism.
[0096]
Embodiment 2
FIG.Embodiment 2 of the present inventionFIG. 6 is a partial enlarged view of the lower part of FIG. 5 showing the entire configuration of the scroll compressor.In the second embodiment,This is a vertically-installed hermetic scroll compressor which is almost the same as in the first embodiment.Since the fixing method in the thrust direction and the lubrication method are different from those in the first embodiment,This difference will be mainly described.
[0097]
The shaft portion 25 and the oil supply hole 32 are integrally formed on the sub rotor member 20 fixed to the main rotor member 7a of the motor.
[0098]
As shown in FIG. 6, a spherical bush 36 whose inner peripheral surface and outer peripheral surface are slidably coupled to each other is disposed on the shaft portion 25, and thrust washers 35a and 35b are disposed at both ends thereof. This is used for positioning the spherical bush 36. The spherical bush 36 is rotatably supported by a spherical bearing 37 fitted to a bearing holding member 39.
[0099]
The spherical bearing 37 is fixed to a bearing holding member 39 by a fixture 38. The bearing holding member 39 is screwed to the auxiliary bearing support plate 24. Therefore, when the bearing holding member 39 is moved up and down, the main rotor member 7a is also moved up and down. Further, since the lever member 6 also slides on the inner peripheral portion of the spherical bush 16 of the lower spherical bearing 17, the lever member 6 is moved. Changes the inclination angle θ. Then, the position of the main rotor member 7a of the motor 7 is fixed by tightening the lock nut 29 at a position where the gap between the orbiting scroll 2 and the fixed scroll 1 becomes appropriate.
[0100]
According to the second embodiment, during operation, the thrust force acting due to the weight of the main rotor member 7a of the motor 7 is received by the thrust washers 35a and 35b, so that a more stable operation of the compressor can be maintained.
[0101]
Since the auxiliary rotor member 20 rotatably supports the lever member 6 via the elastic member 19, the centrifugal force of the lever member 6 itself and the elastic member 19 (see FIGS. 3 and 4) during normal operation. The lever member 6 is constantly pressed outward in the radial direction by the elastic force, and maintains a constant inclination angle θ.
[0102]
An oil supply hole 32 is provided in the sub rotor member 20 and communicates with an oil supply hole 31 formed in the axis of the lever member 6 and an oil supply hole 33 provided in the main rotor member 7a.
[0103]
The oil supply hole 33 reaches the shaft portion 22 above the main rotor member 7a, and is open so as to lubricate a mating bearing surface formed by a hole of a boss below the frame 3.
[0104]
On the other hand, the lubrication hole 31 in the lever member 6 is open to the main bearing 15, and this spherical bearing portion is alwaysCan refuel,Increased bearing reliabilityCan be maintained.
[0105]
FIG. 7 is a view showing the shape of the lever member 6 and an oil supply hole, and FIG. 8 is a sectional view taken along the line CC of FIG. The lever member 6 is generally a round bar shaft, a spherical portion 6a is formed at one axial end and a spherical portion 6c is formed near the axial end, and a cylindrical surface portion is formed at the other axial end. 6b are formed.
[0106]
The spherical portion 6a at one shaft end forms a spherical pair with the slewing bearing 18 shown in FIG. 5, the spherical portion 6c forms a spherical pair with the main bearing 15, and the cylindrical bush 6b at the other shaft end has a spherical bush. The spherical bush 16 is attached to the lower spherical bearing 17 to form a spherical pair.
[0107]
An oil supply hole 31 is formed in the axis of the lever member 6 from one end surface to almost the other end surface. The oil supply hole 31 further branches from the oil supply hole 31 in the spherical portion 6c and the cylindrical surface portion 6b in the radial direction to reach the respective peripheral surfaces. One oil supply hole 31a and 31cOrA plurality is provided.
[0108]
As shown in FIG. 8, an oil supply groove 31b is provided on the peripheral surface of the spherical portion 6c. Similarly, an oil supply groove 31d is provided on the peripheral surface of the cylindrical surface portion 6b.
[0109]
FIG. 9 shows a state in which the spiral member 101 is loaded at the tip of an oil supply hole 32 provided in the axis of the shaft portion 25 of the sub rotor member 20 shown in FIG.Is shown.The spiral member 101 is inserted from the tip of the shaft portion 25 and is prevented from falling off by the support member 102. The spiral member 101 makes it easy for the lubricating oil 8 at the bottom of the compressor to flow into the oil supply hole as the auxiliary rotor member 20 rotates. Since the lubricating oil 8 is sucked up along the spiral member 101, it is particularly effective when the compressor is operated at a low speed.
[0110]
Embodiment 3
Example of the above1,2In the description of the verticalscrollThe present invention has been described with respect to a horizontal compressor.scrollFor compact compressorsApplicable.
[0111]
FIG. 10 shows the vertical installation shown in FIG.scrollType compressor remodeled horizontallyIt is a figure showing Example 3 of the present invention.
[0112]
This horizontalscrollThe type compressor has the same components as those shown in FIG. 5 except for the structure of the lubrication system. The description of the mechanical configuration is omitted, and only the lubrication system will be described.
[0113]
As shown in FIG. 10, a part of the auxiliary bearing support plate 24 is immersed in the lubricating oil 8 stored in the lower part of the body of the closed container 9. Therefore, the lubricating oil path starts from the auxiliary bearing support plate 24.
[0114]
This point is the vertical arrangement shown in FIGS.scrollThis is different from the axial compressor in that the shaft portion 25 of the sub rotor member 20 is the starting point of the lubricating oil path. On the right side in the drawing, oil supply holes 96m, 96l, 96k, 96j, 32 are respectively formed from the auxiliary bearing support plate 24 to the shaft portion 25 of the sub-rotor member 20 via the bearing holding member 39, the spherical bush 36, and the spherical bearing 37. Provided.
[0115]
The lubricating oil 8 passes through these oil supply holes, flows from the oil supply holes 32 of the shaft portion 25, one from the lower spherical bearing 17 through the spherical bush 16, and flows into the oil supply hole 31 provided in the lever member 6, and the other to the main rotor It flows into the oil supply hole 33 provided in the member 7a and reaches each sliding portion. The oil supply path on the upstream side from the oil supply hole 32 of the shaft portion 25 is the same as that shown in FIG.
[0116]
Embodiment 4
FIG.Embodiment 4 of the present inventionHorizontal installation with refueling pumpscrollFIG. 12 is a detailed view of an oil supply pump portion, and FIG. 13 is a sectional view taken along line DD of FIG.
[0117]
thisscrollThe mechanical configuration of the compressor is almost the same as that shown in FIG.So you can seeOnly the lubrication system will be described.
[0118]
In the fourth embodiment, fixed at the bottom of the compressor in which the lubricating oil 8 is stored.scroll1 supports the main bearing 15 of the head plate 1b and the lever member 6 which is supported by a pair of spherical surfaces.flameTurning with 3scrollIn the space surrounded by the second end plate portion 2bscrollThe piston member 105 and the spring member 106 which are in contact with the side outer peripheral surface 2c of the second end plate portion 2b and the pump member 110 which accommodates those members and is constituted by a housing member 109 having an oil suction port and an oil discharge port are provided. A refueling pump is provided.
[0119]
As shown in FIG. 12, the oil suction port and the oil discharge port of the pump chamber 110 are fluiddiodeWithport107 and 108, which branch off from the pump chamber 110 and pass through the lubricating oil 8 at the bottom of the compressor.motorA communication pipe 111 extending to a position higher than the axis 117 and opening is provided.
[0120]
Inhalationport107 is a tapered taper channelThat is,Formed fluid diodepieceConsists offlame3 is fixed to a hole 3a. InhalationportSuction at outlet of 107aspace115 is provided and this suctionspace115 and the pump chamber 110 communicate with each other. vomitport108 also forms a fluidic diode, which is provided at the tip of the piston member 105.
[0121]
This fluiddiodeDischarge withport108 turnsscrollIs in contact with the outer peripheral surface 2c of the end plate 2b, but the outer peripheral surface 2c of the end plate 2bspace116 is provided.spaceTurn from 116scrollAn oil supply hole 96n is formed toward the center of the second end plate portion 2b.
[0122]
The piston member 105 pivots as shown in FIG.scrollThe second end plate 2a is provided with a side outer peripheral surface 2c parallel to the center axis of rotation, and the tip of the piston member 105 is in contact with the end plate 2a.
[0123]
With the above configuration, turningscrollWhen the piston 2 revolves, the piston member 105 in contact with the end plate 2b reciprocates and functions as a pump. When the piston member 105 rises due to the pumping action and the volume in the pump chamber 110 tends to increase,portThe lubricating oil 8 accumulated at the bottom of the compressor is sucked from the pump chamber 110 into the pump chamber 110.
[0124]
Simultaneous discharge at this timeport108 also sucks in the lubricating oil 8 sent to the upstream side,spaceThe flow of the lubricating oil 8 expanded at 116 is a fluiddiodeDischarge withportFlow contracts at the leading edge of 108, where a large flow resistance is generated, and it becomes difficult for the lubricating oil 8 to flow back into the pump chamber 110.
[0125]
Therefore, the lubricating oil 8 is inhaled in many proportions.portIt is sucked from 107.
[0126]
When the piston member 105 descends to reduce the volume in the pump chamber 110,portTurn from 108scrollThe lubricating oil 8 is discharged to the inside of the oil supply hole 96n.
[0127]
At this time, inhalationportAttempt to return lubricating oil 8 from 107spaceThe flow of the lubricating oil 8 expanded at 115 is a fluiddiodeInhalation withportFlow contracts at the leading edge of 107, and a large flow resistance is generated there, making it difficult for the lubricating oil to flow backward.
[0128]
Therefore, lubricating oil 8 is fluiddiodeDischarge withport108, and flows into the oil supply hole 31 inside the lever member 6 through the oil supply hole 96n.
[0129]
As a result, through the respective oil supply holes 31a and 31c (see FIG. 7) branched from the oil supply hole 31, the spherical pair of the spherical portion 6c of the lever member 6 and the main bearing 15, the cylindrical surface portion 6b of the lever member 6, and the spherical bushing. Lubricating oil is supplied to a pair of the lower spherical bearing 17 and the lower spherical bearing 17.
[0130]
The spherical bush 16 is provided with a lubrication hole 96e in the radial direction, and the lower spherical bearing 17 is similarly provided with a lubrication hole 96f.
[0131]
Further, the lubricating oil 8 supplied to the lubrication hole 31 flows through the lubrication hole 96 e of the spherical bush 16 and the lubrication hole 96 f of the lower spherical bearing 17 to flow into the lubrication hole 32 formed in the sub-rotor member 20. The portion is branched and supplied to a sliding portion between the shaft portion 22 at one end of the main rotor member 7a and the hole of the frame 3 through an oil supply hole 33 in the main rotor member 7a of the motor 7, and the other is a sub rotor member. Spherical bushing 36 supporting spherical member 20 and spherical bearing 37 are supplied to a pair.
[0132]
In particular,At the time of high-speed rotation, during the pump suction stroke in which the volume in the pump chamber 110 becomes large, the gas inside the compressor is sucked from the upper end opening of the communication pipe 111 and mixed into the lubricating oil 8 as air bubbles. Due to the nature, the pressure fluctuation in the pump chamber 110 is reduced. This is effective when the cross-sectional area of the communication pipe 111 is small and the length is long.
[0133]
On the other hand, during low-speed rotation, the pressure fluctuation in the pump chamber 110 becomes slow, so that the inside of the communication pipe 111 is filled with lubricating oil.
[0134]
At the time of the pump discharge stroke in which the volume of the pump chamber 110 is small, the amount of oil flowing out of the communication pipe 111 is small due to the resistance of the pipe in the communication pipe 111, so that the pump is turned.scrollA sufficient amount of oil is supplied to each sliding surface in the compressor through an oil supply hole 96n formed in the second end plate portion 2b.
[0135]
Open the upper end opening of the communication pipe 111motorPosition higher than the rotation axisThenA head equivalent to the opening at the upper end is added to the loss resistance of the communication pipe 111, and the same effect as when the cross-sectional area of the pipe is reduced is obtained.
[0136]
FIG. 14 shows pivoting with the lever member 6.scrollFIG. 2 is a diagram showing the refueling of the pair of spherical and two supporting portions. In FIG. 14, the spherical portion 6a of the lever member 6 pivots via the pivot bearing 18.scroll2 is in contact with the boss 2d. TurningscrollThe lubricating oil 8 supplied from the oil supply hole 96 n in the inside 2 is supplied to a sliding portion between the spherical surface portion 6 a of the lever member 6 and the swing bearing 18.
[0137]
On the outer periphery of the slewing bearing 18stickerA member 121 is provided,scrollThe lubricating oil 8 supplied from the oil supply hole 96n inside 2 isstickerBy member 121stickerTurning by actionscrollSince the oil flows into the oil supply hole 31 inside the lever member 6 through the space 127 inside the second boss 2d, it is possible to surely supply oil to each sliding portion inside the compressor.
[0138]
Embodiment 5
FIG. 15 is a view showing a fuel supply path in a compressor using a solid main rotor member instead of the hollow main rotor member of the motor 7 in the scroll compressor shown in FIG. 10 according to a fifth embodiment of the present invention. It is.
[0139]
Inside the main rotor member 7a of the motor 7, a hole portion 120 having a minimum necessary gap into which the lever member 6 is inserted, an oil supply hole 32 inside the sub rotor member 20, and a space on the shaft portion 22 side of the main rotor member 7a. And an oil supply hole 33 communicating with the oil supply port.
[0140]
Oil supply hole 33 inside main rotor member 7a communicating with oil supply hole 32 inside sub-rotor member 20motorDue to the centrifugal force and the pressure difference caused by the inclination with respect to the rotating shaft, the lubricating oil 8 collected at the bottom of the compressor is supplied with the lubrication hole 96m inside the auxiliary bearing support plate 24, the lubrication hole 96l inside the bearing holding member 39, the spherical bearing 37 Through the oil supply hole 96k inside, the oil supply hole 96j inside the spherical surface 36, and the oil supply hole 32 in the sub-rotor member 20, it is necessary and sufficient for each sliding portion in contact with the space on the shaft portion 22 side of the main rotor member 7a and the lever member 6. It is possible to supply only a small amount,flame3 and the shaft portion 22 of the main rotor member 7a in contact with the boss portion 3a are lubricated.
[0141]
Since the oil supply hole 33 inside the main rotor member 7a has a linear shape, the processing is easy. Further, by providing a hole 120 having a minimum necessary gap into which the member 6 is inserted inside the main rotor member 7a,motor7 to secure the magnetic flux density of the magnetic fieldmotorIt is possible to maintain efficiency.
[0142]
Embodiment 6
FIG.Embodiment 6 of the present inventionFIG. 17 is a sectional side view showing a rolling piston type compressor, and FIG. 17 is a sectional view taken along line EE in FIG.
[0143]
This compressor includes a compression mechanism, a compressor driving motor, and a rotor of the motor from one end (left side in FIG. 16) to the other end (right side in FIG. 16) in a cylindrical chamber placed horizontally. The bearings are arranged and arranged sequentially.
[0144]
The cylinder 51 constituting the compression mechanism has a cylindrical hole 51a at the center, and a first plate member 52 and a second plate member 53 are fixed at both ends by bolts 54 so as to close the ends. I have.
[0145]
At this time, the central axis of the hole 52b formed in the boss 52a at the center of the first plate member 52 is fixed so as to be coaxial with the central axis of the cylindrical hole 51a of the cylinder 51. The outer peripheral portion of the cylinder 51 is fixed to the chamber 55. An auxiliary bearing support plate 57 forming a bearing of the stator 56 of the compressor driving motor and the rotor 65 of the compressor driving motor is also fixed to the chamber 55.
[0146]
A boss 57a is formed at the center of the auxiliary bearing support plate 57, and a cylindrical hole 57b is formed at the tip thereof.
[0147]
The central axis of the cylindrical hole 57b is coaxial with the central axis of the hole 52b at the center of the first plate member 52.
[0148]
The main rotor member 58 of the compressor driving motor has a hollow cylindrical shaft portion 58a formed on one end side, and a permanent magnet 59 fixed to the outer peripheral portion. A cavity 60 is formed inside the main rotor member 58, and the cavity 60 is connected to a hollow portion of the shaft portion 58a on one end side.
[0149]
However, the cavity 60 is desirably minimized in order to maintain the function of the motor at a high level, and it is sufficient that the cavity 60 has a size in which the lever member 72 can be arranged.
A sub-rotor member 61 is attached to the other end of the main rotor member 58 of the compressor driving motor integrally with the main rotor member 58.
[0150]
The auxiliary rotor member 61 has a shaft 61a extending toward the other end, and a hole 61b opening toward the cavity 60 is formed so as to be deviated from the center axis of the shaft 61a in the radial direction. . A spherical support member 62 (third spherical bearing) having an outer cylindrical surface and an inner spherical surface is inserted into the hole 61b, and the spherical bush 63 having an outer spherical surface and an inner cylindrical surface by the spherical support member 62. Are supported to form a so-called spherical bearing. The spherical support member 62 is elastically supported by the elastic member 19.
[0151]
The main rotor member 58 and the sub rotor member 61 are integrally connected by bolts 64 or the like so that their shaft portions 58a and 61a are coaxial with each other to form a rotor portion 65 of the compressor driving motor. . The rotor portion 65 has two shaft portions 58a and 61a at each end rotatably fitted into the hole portion 52b of the first plate member 52 and the hole portion 57b of the auxiliary bearing support plate 57, respectively. Supported.
[0152]
A thrust plate 67 mounted on the tip of the shaft portion 61a of the sub-rotor member 61 so as to rotate together with a key 66 is in contact with a thrust bearing 68, and the stator portion 56 and the rotor portion of the compressor driving motor are provided. Since the respective magnet centers 69 and 70 are deflected in the axial direction with respect to each other, a magnetic force in a direction in which the thrust plate 67 and the thrust bearing 68 come into contact with the rotor portion 65 always acts on the rotor portion 65. Is determined by the axial position of the thrust bearing 68.
[0153]
The thrust bearing 68 has a thread formed on its outer periphery, is screwed into the auxiliary bearing support plate 57, adjusts its axial position, and is finally fixed by the lock nut 71.
[0154]
That is, the axial position of the rotor section 65 can be adjusted. This changes the inclination angle of the lever member 72 as described in the first embodiment.
[0155]
The lever member 72 has a spherical portion 72a (first spherical portion) at one end, a cylindrical surface portion 72b at the other end, and another spherical portion 72c (second spherical portion) intermediate the two. The axis connecting the ball center of the portion 72a and the ball center of the spherical portion 72c is the central axis of the cylindrical surface portion 72b.
[0156]
The lever member 72 has a cylindrical surface portion 72b rotatably fitted into the inner peripheral cylindrical surface portion of the spherical bush 63 and supported by bearings. The spherical portion 72c has an outer peripheral cylindrical surface portion and an inner peripheral spherical portion, and has a hole 52b of the first plate member 52. Are supported by a pair of spherical surfaces by a spherical support member 73 (second spherical bearing) inserted and fixed in the pair.
[0157]
A cylindrical roller 74 has an outer cylindrical surface and an inner spherical surface on the spherical portion 72 a of the lever member 72, and is provided via a spherical support member 75 (first spherical bearing) inserted into the inner cylindrical surface of the roller 74. It is supported by a spherical pair.
[0158]
The lever member 72 is formed such that the distance between the center of the spherical portion 72c and the cylindrical surface portion 72b is sufficiently larger than the distance between the center of the spherical portion 72c and the center of the spherical portion 72a.
[0159]
Each of the spherical support members 62, 73, and 75 has a structure that can be divided in the radial direction.
[0160]
The rotation speed of the lever member 72 is very low compared to the rotation speed of the rotor portion 58 of the motor.
[0161]
As a result, even if the load is large on the spherical surface portion 72a and the spherical surface portion 72c, the relative sliding speed is small, and the relative sliding speed is relatively high on the cylindrical surface portion 72b, but the applied load is small.
[0162]
Therefore, should a material with excellent lubrication properties be applied to these spherical pair parts?,By performing a surface treatment such as coating a material having self-lubricating properties, the compressor can be operated without oil lubrication.
[0163]
A vane 76 is integrally fixed to one portion of the outer periphery of the roller 74 by welding or the like. At this time, two parallel planes of the vane 76 are fixed so as to be parallel to the central axis of the roller 74. I have.
[0164]
Outside the cylindrical inner peripheral surface 51a of the cylinder 51, a cylindrical hole 51b having a central axis parallel to the central axis of the cylindrical inner peripheral surface 51a is formed. The sides communicate with a space at the center of the cylinder and another space 77 provided outside the cylindrical hole 51b.
[0165]
The vane 76 is inserted into the cylindrical hole 51b and the space 77. Between the vane 76 and the cylindrical hole 51b, a plane portion slidably in contact with the plane portion of the vane 76 and the cylindrical surface of the cylindrical hole 51b. A sliding member 78 having a cylindrical surface portion slidably in contact with the vane 76 is incorporated with the vane 76 interposed therebetween.SaidIt is supported by a cylinder 51 so as to be able to swing around a central axis.
[0166]
The tip of the vane 76 on the side opposite to the joint with the roller 74 moves in the space 77 and does not interfere with the cylinder 51.
[0167]
With the above configuration, when the rotor 65 of the compressor driving motor rotates, the cylindrical surface 72b is supported at a position deviated from the rotation axis of the rotor 65, and the spherical surface 72c is moved.SaidThe center axis of the lever member 72 supported by a pair of spherical surfaces about a point on the rotation axis has a constant inclination angle with respect to the rotation axis of the rotor unit 65, and has two conical shapes having the apex at the center of the pair of spherical surfaces. Draw the trajectory of
[0168]
Therefore, the center of the spherical portion 72a of the lever member 72 performs a circular motion, and the roller 74 supported by the spherical pair by the spherical portion 72a is revolved.
[0169]
Since the position of the rotor portion 65 can be adjusted in the axial direction, the inclination angle of the center axis of the lever member 72 with respect to the rotation axis of the rotor portion 65 can be adjusted, and the revolution radius of the roller 74 can be reduced.Can be adjusted.That is, the gap between the outer cylindrical surface of the roller 74 and the inner cylindrical surface 51a of the cylinder can be adjusted.
[0170]
A first side chamber 79 and a second side chamber 80 are welded to each end opening of the chamber 55, respectively, to form a closed container as a whole.
[0171]
The working gas flows into the compressor from the suction port 81, passes through the suction passage 51 c formed in the cylinder 51, and is sucked and compressed in the compression chamber by the increase or decrease in the volume of the compression chamber, and is formed on the second plate member 53. A discharge port (not shown) discharges through a discharge valve 82 and a discharge valve holder 83. Thereafter, the fluid flows out of the compressor through a discharge port 84 provided in the second side chamber 80 through the motor chamber.
[0172]
The load acting on the spherical portion 72a of the lever member 72 due to the pressure of the compressed gas acting on the outer periphery of the roller 74 is supported by the lever member 72 being restrained by the other components at the spherical portion 72c and the cylindrical surface portion 72b. However, if it is considered that the center of the spherical portion 72a is the load point, the center of the spherical portion 72c is the fulcrum, and the center of the spherical bush 63 supporting the cylindrical surface portion 72b is the power point, in the present embodiment, compared with the distance between the fulcrum and the load point. Since the distance between the fulcrum and the force point is sufficiently large, the magnitude of the load acting on the force point is greatly reduced by the principle of leverage as compared with the magnitude of the load acting on the load point.
[0173]
During normal operation, the lever member 72 maintains the maximum inclination angle due to the centrifugal force of the lever member 72 itself and the elastic member 19.
[0174]
However, if the pressure in the compression chamber rises abnormally as in the previous embodiment,SaidDue to the arrangement of the elastic member 19, the inclination angle of the lever member 72 is reduced, and the minimum clearance between the cylinder 51 and the roller 74 is larger than that during normal operation.
[0175]
Therefore, according to the present embodiment, the pressure in the compression chamber is quickly reduced, and operation in an overload state can be avoided, and the vane 76 can be prevented from being broken or deformed, and from damage to other moving parts.Can be prevented.
[0176]
Embodiment 7
FIG.Embodiment 7 of the present inventionFIG. 19 is a view showing the overall configuration of the hermetic positive displacement compressor, and FIG.
[0177]
The seventh embodiment is also a compressor of the same type as the rolling piston compressor, and the compression mechanism is changed in the embodiment shown in FIG.This is an example.In the following description, points different from the embodiment of FIG. 16 will be described.
[0178]
Reciprocable to cylinder 51likeThere is a fitted vane member 90, and a preload spring 93 is arranged behind the vane member 90.
For this reason, the other end surface of the vane member 90 is pressed against the outer peripheral surface of the roller 91 to separate the compression working chamber into a suction chamber and a compression chamber.
[0179]
Since the space 57 communicates with the discharge pressure space in the sealed container 79, the pressure in the space 57 is also as high as the same.
Therefore, the vane 90 is pressed against the roller 74 by this pressure. Furthermore, since the other side of the lever member 72 is pressed radially outward by the elastic member 19, the inclination angle of the lever member 72 is maintained at the maximum.
[0180]
As described above, in the seventh embodiment, during normal operation of the compressor,OrIn a rated operation state or the like, the minimum gap between the inner surface of the cylinder 51 and the outer peripheral surface of the roller 91 can be kept small. As a result, the performance of the compressor can be kept high.
[0181]
The effect of the elastic member 19 has an effect of preventing an abnormal increase in the pressure in the compression working chamber as in the above-described embodiment.
[0182]
【The invention's effect】
According to the present invention, a hermetic positive displacement compressor is a compressor including a compression mechanism having a pair of fixed members forming a compression working chamber and a rotating rotor member, and an electric motor driving the rotating rotor. As a transmission mechanism for connecting the mechanism and the electric motor, a first spherical bearing at a front end portion and a first spherical bearing provided at a position eccentric by a turning radius from a turning center axis at a portion of a turning rotor member are spherically paired, and a middle portion of the intermediate portion is provided. The second spherical portion and the second spherical bearing provided at a fixed point on the motor rotating shaft are spherically coupled, and the first and second portions of the spherical bush and the rotor of the motor are slidably fitted on the round shaft portion at the rear end. A third spherical bearing provided at a position on an extension of a straight line connecting the centers of the two spherical portions is provided with an inclined lever member so as to form a spherical pair with the third spherical bearing. Provided with a mechanism Therefore, when the rotor of the electric motor is moved, for example, in the orbiting scroll direction by the positioning mechanism, the slide-fit spherical bush at the rear end of the lever member moves in the axial direction of the lever member, and the third spherical bearing with respect to the electric motor rotating shaft moves. Since the eccentric distance is constant, the tilt angle of the lever member becomes large, and thus the gap between the fixed member and the turning member becomes larger.Can be made smaller,Adjusted during assembly, independent of the accuracy of the various components of the closed displacement compressorOrThe gap that forms the compression working chamber can be optimized by adjustingCan be maintained,Closed displacement type compressor with low leakage and high performanceCan be provided.
[0183]
In the above-mentioned closed displacement type compressor, when a third spherical bearing is further provided on the rotor of the electric motor with an elastic member being pressed outward in the radial direction of the rotor, the liquid flows together with the sucked gas into the compression working chamber. In addition, the lever member presses the elastic member to change the inclination angle of the lever member, and the gap in the compression working chamber automatically increases, causing an excessive pressure rise.Can be prevented.
[0184]
Further, in the closed type positive displacement compressor,
(A) providing a lubricating path for supplying lubricating oil stored in the bottom of a closed vessel containing a compression mechanism and an electric motor from an oil supply hole formed in a rotor of the electric motor to each sliding surface through an oil supply hole formed in a lever member;Or
(B) a pump mechanism for pumping the outer circumferential surface of the orbiting scroll in accordance with the orbital movement of the orbiting scroll member, and a lubricating oil sucked up from the bottom of the sealed container by means of an oil supply hole formed in the orbiting scroll member through a lever member; By providing a lubrication path to supply to each sliding surface via a lubrication hole formed in
It is possible to supply a necessary and sufficient amount of lubricating oil to each sliding surface, providing high performance and high reliability.scrollShape compressorCan be provided.Compressor componentsCan be simplified and productivity increased.
[Brief description of the drawings]
FIG. 1 shows a first embodiment of the present invention.IsIt is sectional drawing which shows the whole structure of the vertically arranged hermetic scroll compressor.
FIG. 2 is a cross-sectional view showing an engaged state of a scroll member in the cross-sectional view taken along the line AA of FIG. 1;
FIG. 3 is a sectional view showing a bearing mechanism at a lower end portion of a drive shaft (lever member) of the hermetic scroll compressor.
FIG. 4 is a cross-sectional view showing another bearing mechanism at the lower end of the drive shaft (lever member) of the hermetic scroll compressor.
FIG. 5 shows a second embodiment of the present invention.IsIt is sectional drawing which shows the whole structure of a vertical installation hermetic scroll compressor, and a lubrication oil supply system.
FIG. 6 is a partial sectional view showing a mechanism for adjusting a tilt angle of a lever member.
FIG. 7 is a view showing a lever member.
FIG. 8 is a sectional view taken along line CC of FIG. 7;
FIG. 9 is a view showing an oil supply mechanism in which a spiral member is provided in a lubrication oil supply hole.
FIG. 10 shows a third embodiment of the present invention.IsIt is sectional drawing which shows the whole structure of a horizontally-mounted hermetic scroll compressor, and a lubrication oil supply system.
FIG. 11 shows a fourth embodiment of the present invention.IsIt is sectional drawing which shows the whole structure of a horizontally-mounted hermetic scroll compressor, and a lubrication oil supply system.
12 is a partial view of FIG. 11 and is a configuration diagram of a refueling pump.
FIG. 13 is a view for explaining the operation of the oil supply pump in the cross-sectional view taken along the line DD in FIG. 11;
FIG. 14 is a view showing a seal of a bearing portion between the lever member and the orbiting scroll.
FIG. 15 shows a fifth embodiment of the present invention.IsIt is sectional drawing which shows the whole structure of a horizontally-mounted hermetic scroll compressor, and a lubrication oil supply system.
FIG. 16 shows a sixth embodiment of the present invention.IsIt is sectional drawing which shows the whole structure of a sealed rotary compressor.
FIG. 17 is a sectional view showing a section taken along line EE of FIG. 16;Is.
FIG. 18 shows a seventh embodiment of the present invention.IsIt is sectional drawing which shows the whole structure of a sealed rotary compressor.
19 is a sectional view taken along line FF of FIG. 18;
[Explanation of symbols]
1 fixed scroll
1a Scroll wrap
1b End plate
2 orbiting scroll
2a Scroll wrap
2b head plate
3 frames
6 Lever members
6a, 6c Spherical part
6b Cylindrical surface
7 Motor
7a Main rotor member of motor
7b Stator of motor
8 Lubricating oil
9 Closed container
10 Compression working chamber
11 Suction pipe
12 Discharge port
13 Discharge pipe
15 Main bearing
16 Spherical bush
17 Lower spherical bearing
18 Slewing bearing
19 Elastic member
20 Sub rotor member
22 Shaft
23 Slide bearing
24 Auxiliary bearing support plate
25 Shaft
26 Thrust plate
31, 32, 33 Oil hole
36 spherical bush
39 Bearing holding member
51 cylinder
52 First plate member
53 Second plate member
55 chambers
56 Stator of motor
57 Auxiliary bearing support plate
58 Main rotor member
61 Sub rotor member
62 Spherical support member
63 spherical bush
65 Motor rotor
67 Thrust plate
68 Thrust bearing
72 Lever member
72a spherical surface
72b cylindrical surface
72c spherical surface
73 Spherical support member
74 rollers
75 Spherical support member
76 Vane
78 Sliding member
81 Inlet
82 Discharge valve
84 Discharge port
90 Vane
91 rollers
93 Preload spring
96a Oil supply hole
96n oil supply hole
101 spiral member
102 Supporting member
105 Piston member
106 spring member
107 Oil inlet
108 Oil outlet
107a fluiddiodeWith inhalationport
108a fluiddiodeWith dischargeport
110 pump room
111 communication pipe
112a, 112bTaperChannel
114 inhalationpiece

Claims (8)

In a sealed container, a compression mechanism having a pair of fixing members and the orbiting rotor member forming a compression operation chamber, was placed an electric motor having a rotary shaft to pivot axis coaxial with the pivot rotor driving the compression mechanism In a hermetic type displacement compressor, as a transmission mechanism for transmitting a driving force of an electric motor to a compression mechanism, an end portion is eccentrically shifted by a turning radius from a rotating shaft of the electric motor, connected to a turning rotor member in a spherical pair, and an intermediate portion is connected to the electric motor. The spherical end is supported at a fixed point on the rotation axis of the motor, and the rear end is positioned at a position on the extension of a straight line connecting the center point of the spherical pair at the front end and the fixed point at the portion of the rotor of the motor. A closed displacement type compressor comprising a lever member to be connected, and a tilt angle adjusting mechanism for changing a tilt angle of the lever member with respect to a rotation axis of the electric motor. In a sealed container, a compression mechanism having a pair of fixing members and the orbiting rotor member forming a compression operation chamber, was placed an electric motor having a rotary shaft to pivot axis coaxial with the pivot rotor driving the compression mechanism In a hermetic type displacement compressor, as a transmission mechanism for transmitting a driving force of an electric motor to a compression mechanism, an end portion is eccentrically shifted by a turning radius from a rotating shaft of the electric motor, connected to a turning rotor member in a spherical pair, and an intermediate portion is connected to the electric motor. Lever is supported at a fixed point on the rotation axis of the motor, and the rear end of the motor is connected to the rotor of the motor by making a spherical pair at a position on the extension of the fixed point and the center of the spherical pair at the tip. A closed displacement positive displacement compressor comprising a member and a turning radius adjusting mechanism for changing a turning radius of the turning rotor member. A hermetic positive displacement compressor including a compression mechanism having a pair of fixed scrolls and a orbiting scroll forming a compression working chamber in a closed container , and an electric motor having a rotation axis arranged coaxially with a center axis of the orbiting scroll. Wherein a first spherical portion formed at the front end and a first spherical bearing provided at a position eccentric by a turning radius from a turning center axis at a turning scroll portion as a transmission mechanism for transmitting the driving force of the electric motor to the compression mechanism. A spherical bush slidably fitted to a round shaft portion formed at a rear end portion, wherein a second spherical portion formed at an intermediate portion and a second spherical bearing provided at a fixed point on a rotating shaft of the motor are spherically paired; A lever member inclined with respect to the rotation axis of the motor, wherein a third spherical bearing provided at a position on an extension of a straight line connecting the centers of the first spherical portion and the second spherical portion at the portion of the rotor of the motor is spherically coupled. And further A positioning mechanism for positioning the rotor of the motor is moved in the rotation axis direction, sealed displacement type compressor, characterized by comprising a support mechanism for supporting the second spherical bearing. The hermetic positive displacement compressor according to claim 3 , wherein an elastic member for pressing a third spherical bearing outward in a radial direction of the rotor is provided on a rotor of the electric motor. The hermetic type displacement compressor according to claim 4 , wherein the lever member has a distance from the second spherical portion to the spherical bush larger than a distance from the second spherical portion to the first spherical portion. A compression mechanism having a cylinder fixed in an airtight container , a roller rotating in the cylinder, and a vane forming a compression working chamber by partitioning a space between the cylinder and the roller, and coaxially with a rotation center axis of the roller. In a hermetic type displacement compressor having a motor having a rotating shaft disposed therein, as a transmission mechanism for transmitting a driving force of the motor to a compression mechanism, a first spherical portion formed at a front end and an inner peripheral cylinder formed by a roller. A first spherical bearing provided in the plane is spherically paired, a second spherical part formed in the intermediate part and a second spherical bearing provided at a fixed point on the rotating shaft of the motor are spherically paired, and a rear end part is formed. The spherical bush slidingly fitted on the formed round shaft portion and a third spherical bearing provided at a position on an extension of a straight line connecting the centers of the first spherical portion and the second spherical portion at the portion of the rotor of the electric motor. To the rotating shaft of the motor A closed-type positive displacement type in which a lever mechanism is provided, which is provided with a tilting lever member, and a positioning mechanism for moving and positioning the rotor of the electric motor in the direction of the rotation axis, and a supporting mechanism for supporting the second spherical bearing. Compressor. 7. The hermetic positive displacement compressor according to claim 6, wherein an elastic member for pressing a third spherical bearing outward in a radial direction of the rotor is provided on a rotor of the electric motor. 8. The hermetic positive displacement compressor according to claim 7, wherein the lever member has a distance from the second spherical portion to the spherical bush larger than a distance from the second spherical portion to the first spherical portion.

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