JPH01290983A - Scroll type hydraulic machine - Google Patents

Abstract

PURPOSE:To lubricate an anti-rotation mechanism sufficiently, by arranging a thrust plate between a bearing support and a movable side scroll member and providing a refrigerant gas flow path in the back face of the movable side scroll member. CONSTITUTION:Pins 51 are provided to fixed side and movable side thrust plates 53, 55. When a crankshaft 13A rotates, rotation of the movable side scroll member 41 is suppressed through a plurality of pins 51 arranged in the circumferential direction. Approximately semi-circular notches 53b, 55b are made respectively in the fixed side and the movable side thrust plates 53, 55. A refrigerant gas flow path 57 communicated with a motor section space 26 is formed at each position of a bearing supporting board 7 corresponding to the notches 53b, 55b.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a closed scroll fluid machine used in air conditioners, refrigeration equipment, etc.

(Prior Art) As a conventional scroll fluid machine, there is a scroll type electric compressor using a spiral scroll member.

In this type of electric compressor, a crankshaft is provided eccentrically to the drive shaft of an electric motor, and a movable scroll member is connected to the crankshaft. As the drive shaft rotates, the movable scroll member moves eccentrically and compresses refrigerant gas in a plurality of compression chambers formed between the movable scroll member and the fixed scroll member fixed to the case.

In addition, in order to prevent rotational movement of the movable scroll member during eccentric movement, a rotation prevention mechanism using, for example, a ball bearing is provided between the movable scroll member and the case. This prevents the movable scroll section from rotating when the machine is driven.

The rotation prevention mechanism using ball bearings uses two thrust plates that guide the eccentric movement of the balls (for example, Japanese Patent Publication No. 60-22199).

(Problem to be Solved by the Invention) However, in the electric compressor using the ball bearing rotation prevention mechanism described above, each thrust plate simply guides the balls, and the case side and the movable scroll member Since each ball itself directly receives the thrust force acting during the point contact, the wear of each ball becomes significant and it is difficult to ensure smooth movement of the bearing portion.

Therefore, in the present invention, a rotation prevention mechanism using a pin is used,
The object of the present invention is to provide a scroll fluid machine in which the thrust force acting directly on the pin is alleviated, damage and wear of the pin is prevented, and the anti-rotation mechanism is sufficiently lubricated.

(Means for Solving the Problems) A scroll fluid machine of the present invention includes, in a sealed case, an electric motor, a bearing support member fixed to the case and supporting an upper part of the drive shaft of the electric motor, and the drive shaft. a crankshaft that is eccentric with respect to the drive shaft; a fixed scroll member that is fixed to the case; A movable scroll member that rotates, a rotation prevention mechanism that prevents rotation of the movable scroll member, and a flow passage provided in the bearing support member that allows refrigerant gas to flow from the electric motor side to the scroll member side. and the rotation prevention mechanism includes an annular fixed thrust plate fixed to the bearing support member, and an annular movable thrust plate fixed to the movable scroll member and in surface contact with the fixed thrust plate. , and a pin inserted into the holes of both of the thrust plates, and the flow path provided in the bearing support member is provided so as to face the back surface of the movable scroll member.

(Operation) The drive shaft rotates due to the drive of the electric motor, and the crankshaft performs eccentric movement accordingly. Due to the eccentric movement of the crankshaft, the movable scroll member connected to the crankshaft moves eccentrically while meshing with the fixed scroll member, and refrigerant gas is compressed in a compression chamber formed between both scroll members.

The above-mentioned refrigerant gas once collides with the back surface of the movable scroll member from the electric motor side through the flow path, and is passed to both scroll members. Therefore, at the time of collision, oil separation in the refrigerant gas is performed, and the separated oil is is supplied to the rotation prevention mechanism to provide sufficient lubrication. In addition, in this case, the thrust force acting between the case side and the movable scroll member is
Since it is received by both thrust plates that are in surface contact with each other, no weight is applied to the pin that connects them, and damage to the pin can be prevented.

(Example) An embodiment of the present invention will be described below based on the drawings.

FIG. 1 shows a scroll type hermetic electric compressor (scroll fluid machine) 1, in which 3 and 5 are an upper case and a lower case, and 7 is a bearing support plate. The upper case 3 and the lower case 5 are connected to each other with a bearing support plate 7 and a shim 9 interposed therebetween by a plurality of bolts 11 so that the inside thereof is sealed. The shim 9 is provided to adjust the axial dimension.

Above case 3. A drive shaft 13 is disposed in the vertical direction inside S, and the lower part of the drive shaft 13 is connected to the lower case 5 via a bearing 15.
The upper part of the drive shaft [3] is supported by a bearing member 7 via a bearing 17. In addition, 19 in the figure is a stopper ring of the bearing 17.

A columnar rotor 21 made of a laminated iron core is fixed to the lower end side of the drive shaft 13, and a permanent magnet 23 that sequentially constitutes an N pole and an S pole is attached to the circumferential surface of this rotor 21.

Further, a cylindrical stator 25 made of a laminated iron core is disposed on the outer periphery of the permanent magnet 23, and this stator 25 is attached to the lower case 5.
It is fixed at C. As shown in FIG. 2, an excitation coil 27 is wound around each salient pole 25a of the stator 25, and these constitute a brushless electric motor 28. −
The excitation coil 27 is supported by a support member 29 fixed to the lower case 5, as shown in FIG.
The lead wire 33 is connected to the lead wire 33 passing through the wire 1.
is pulled out of case 5 and placed in C.

A suction union 35 is fixed to the upper side of the stator 25 of the lower case 5 through the case 5.
A suction pipe (not shown) is connected to the refrigerant to suck refrigerant. A pipe 37 is connected to the union 35, and a tip end opening 37a of the pipe 37 connects to the space 3 between adjacent salient poles 25a of the stator 25, as shown in FIGS. 1 and 2.
It is bent so that it faces 9.

Therefore, the refrigerant gas is guided from the union 35 through the pipe 37 to the space 39 between the salient poles 25a, as shown by the arrow in FIG. 1, and the stator 25 and the coil 27 are cooled. Furthermore, the refrigerant gas that has passed through the space 39 collides with the inner surface of the bottom of the lower case 5, passes through the gap between the rotor 21 and the stator 25, reaches the upper part, and then returns to the motor 2.
8 cooling is performed. In this case, the refrigerant gas that collides with the bottom of the case turns the oil adhering to the inner surface of the bottom of the lower case 5 into mist (particulates), which flows upward as refrigerant gas mixed with oil mist.

As shown in FIG. 1, the upper end of the drive shaft 13 is integrally formed with a crankshaft 13A whose center 02 is eccentric from the center O0 of the drive shaft 13 by a predetermined distance. This crankshaft 13A is inserted through a metal bearing 43 into a connecting insertion part 41a formed in a concave shape on the back side of the movable scroll member 41, and the crankshaft 13A rotates as the drive shaft 13 rotates. As a result, the movable scroll member 41 is driven to rotate. In addition, since the crankshaft 13A is eccentric with respect to the drive shaft 13, in order to stabilize the rotational balance of the drive shaft 13, the drive shaft 13A is
A balance weight 45 is fixed below the bearing 17 with a screw 47.

As shown in FIGS. 3 and 4, between the movable scroll member 41 and the bearing support plate 7, annular fixed thrust plates 1 to 53 fixed to the bearing support plate 7 and a movable side An annular movable thrust plate 55 fixed to the back surface of the scroll member 41 is interposed so as to be in sliding surface contact with each other. Further, a pin 51 is interposed between both thrust plates 53 and 55. As shown in FIG. 3, the pins 51 are arranged at four locations at equal intervals in the circumferential direction. Further, as shown in FIGS. 5 and 6, the pin 51 is composed of a large diameter portion 51a and a small diameter portion 51b, and the small diameter portion 51b has a circular outer shape in front of the large diameter portion 51b.
The centers of both are shifted by the same dimension as the eccentricity of the crankshaft 13A so as to protrude from the front circular outer shape of the crankshaft 13A. The large diameter portion 51a of each pin 51 is connected to a hole 5 formed in the stationary thrust plate 53.
3a, and the small diameter portion 51b of each pin 51 is fitted into the hole 5 of the movable thrust plate 55.
5a via a metal bearing 56 so as to be rotatable. Therefore, when the crankshaft 13A turns, the rotation of the movable scroll member 41 is suppressed by the plurality of pins 51 arranged in the circumferential direction. That is, the pin 51, both thrust plates 53, 55, and the metal bearing 56 constitute a rotation prevention mechanism 58.

Further, the fixed side and movable side thrust plates 53.
55, substantially semicircular notches 53b and 55b of the same shape are formed, respectively, as shown in FIGS. 3 and 4. This notch 53b.

55b are formed at four locations at equal intervals in the circumferential direction. In addition, a suction bow 1- (refrigerant gas flow path) 57 communicating with the motor section space 26 is formed at each position of the bearing support plate 7 corresponding to these notches 53b and S5b, and each suction boat 57 each.

both thrust plays)-53, 55 notch 53b,
It faces the back surface of the movable scroll member 41 via the movable scroll member 41, and communicates with a suction pressure chamber 65 of the scroll portion of FIG. 1, which will be described later, through these notches 53b and 55b. Therefore, each suction boat 57 can be provided close to the drive shaft 13 so as to communicate with the notches 53b and 55b of both thrust plates 53 and 55.
It becomes possible to reduce the outer diameter of the bearing support plate 7, and accordingly, the outer diameter of the compressor itself can be reduced.

As shown in FIG. 3, the fixed thrust plate 53 and the movable thrust plate 55 are displaced from each other in the rotation direction as the movable scroll member 41 rotates together with the crankshaft 13A. The movable scroll member 41 is in contact over a wide area in the radial direction, making it possible to receive the thrust force acting on the movable scroll member 41 as a small thrust force per unit area. Further, the refrigerant gas in the motor space 26 is transferred from each suction boat 57 to both thrusts 1 through the notches 53 of the sprays 1 to 53.55.
b, 55b to the suction pressure chamber 65 of the scroll portion, but at this time, the fixed side thrust plate 53 and the movable side thrust plate 1 55 are displaced by 1N as shown in FIGS. 3 and 1. As a result, the refrigerant gas that has passed through the notch 53b of the stationary thrust plate 53 collides with a part of the wall of the movable thrust plate 1-55 due to inertial force.
As a result of this collision, mist oil in the refrigerant gas adheres to the
This oil that has arrived flows into the gap between the thrust plates 53 and 55 on the fixed side and the movable side, which provides sufficient lubrication between the two thrust plates 53 and 55, which slide into contact with each other and exert a large thrust force. 55 will slide smoothly. Similarly, the notch 55 of the movable thrust I-plate 55
The refrigerant flowing through b also collides with the back surface of the movable scroll member 41, and the oil adhering to it further flows between both thrust plates 53 and 55 to perform lubrication, and the rotation prevention mechanism 58 will be sufficiently lubricated.

The sliding contact surface of the movable thrust plate 55 that comes into sliding contact with the stationary thrust plate is shown in FIGS. 1, 3, and 7.
As shown in Figures (a) and (b), the annular oil J55
c is formed. This oil groove 55C has all the notches 55b and the recess 55 into which the pin 51 is fitted.
This annular oil groove 55c is connected to four oil grooves 55d provided in the radial direction.
is communicated with.

Therefore, the notches 5 of both thrust plates 53, 55
The oil that enters between them from 3b and 55b lubricates the sliding surfaces of each other through the annular oil groove 55c, and also lubricates the various fitting portions of the pin 51. Furthermore, the oil supplied through the radial oil groove 55d lubricates the space between the crankshaft 13A and the metal bearing 43, thereby ensuring lubrication of each part where stress is concentrated.

In addition, the bearing support plate 7 and the fixed side thrust plate 53
A fan 61 fixed to the drive shaft 13 with screws is provided in a space 59 surrounded by the movable scroll member 41 and the movable scroll member 41 . This fan 61 is installed so that as the drive shaft 13 rotates, air can be blown from the space 59 above C1 to the space 26 on the motor 28 side through the gap between the bearings 17 and the like. 59 becomes negative pressure, and due to the negative pressure, more lubricating oil is supplied between the above-mentioned two thrust plates 53 and 55, thereby improving lubrication.

The movable scroll member 41 supported by the crankshaft 13A is engaged with a fixed scroll member 63 fixed to a plurality of poles 1 in the upper case 3 at 62. For example, as shown in FIG. 1 and FIG. As shown, a suction pressure chamber 65 is formed to have a suction pressure, an intermediate pressure chamber 67 is compressed to an intermediate pressure, and a discharge pressure chamber 69 is compressed to a discharge pressure. 71 is formed, and this discharge boat 71 communicates with a discharge chamber 75 via a reed valve 73. Then, the movable scroll member 41 moves to the fixed scroll member 6 according to the eccentricity of the crankshaft]3A.
A sealed pressure chamber 67. which is formed by sliding and meshing with 3.
The volume of the discharge boat 73 is gradually reduced to compress the refrigerant from the suction pressure to the intermediate pressure and then from the intermediate pressure to the discharge pressure.
, more is discharged. In addition, 76 in the figure indicates a discharge union.

The movable scroll member 41 is provided with extremely small diameter oil holes 77 and 79. One oil hole 77 is
As shown in FIG. 1, one end thereof communicates with the gap between the end face of the crankshaft 13A and the movable scroll member 41, and the other end communicates with both scroll members 4.1 as shown in FIG.
．． Three types of chambers 65, 67, 69 . Among them, intermediate pressure chamber 67
is connected to. Further, as shown in FIG. 1, the other oil hole 79 has one end connected to the stationary thrust plate 5.
3 and the movable scroll part phase 41 [/, and the other end side is also connected to the intermediate pressure chamber 67 as described above.

Also, both of these oil holes 77 and 79 are connected to the intermediate pressure chamber 67.
The position communicating with the fixed side scroll member 63 is selected from the position where the wrap portion 63A of the fixed scroll member 63 communicates with the fixed side scroll member 63 intermittently. The oil that has arrived at the inner wall surface of the intermediate pressure chamber 67 due to the intermediate pressure of the intermediate pressure chamber 67 passes through the oil hole 77 to the end surface of the crankshaft 13A and the movable scroll member 41.
On the other hand, oil is intermittently supplied to the gaps between the stationary thrust plate 53, the movable scroll member 41, and the movable thrust plate 55 through the oil holes 79.

Further, an annular oil reservoir 8 is provided on the upper surface of the fixed scroll member 63 that defines the discharge chamber 75 together with the upper case 3.
1 is formed, and this oil reservoir 81 has a discharge chamber 7.
The oil in 5 is collected. On the other hand, a surface 41b of the movable scroll member 41 facing the fixed scroll member 63
An annular oil groove 83 is formed along its periphery, and oil from the inner surface of the suction pressure chamber 75 is stored in this oil groove 83, and this oil allows the tip of the wrap portion 63A to come into sliding contact when the compressor is driven. Surface lubrication takes place.

Further, the oil reservoir 81 is communicated with an oil hole 85 extending to the peripheral edge of the surface of the fixed scroll member 63 facing the movable scroll member 41 . This oil hole 8
5 is provided with a check valve 87. In this embodiment, the check valve 87 is constituted by a reed valve that opens the oil hole 85 when the pressure in the discharge chamber 75 is low (below the discharge pressure). Therefore, when the compressor is running, the oil hole 85 is closed, and when the compressor is stopped, the oil hole 85 is opened, and the oil in the oil reservoir 81 is guided to the suction pressure chamber 75 through the oil hole 85. This supplied oil travels along the wall surface of the lap portion 41 and is collected in the oil groove 83, and when the compressor is started,
3A lubrication is provided for smooth starting.

In addition, by preparing various plate thicknesses for both of the thrust plates 53 and 55 mentioned above, and selecting and assembling the appropriate thrust plate 531 J 5 when assembling the compressor, it is possible to eliminate machining dimensional errors in the axial direction. It is also possible to easily accommodate the above-mentioned configuration, reduce assembly costs, and create a structure that does not require the shim 9 described above.

By providing the thrust plates in sliding contact with each other between the bearing support member and the movable scroll member in this way, only a small thrust force acts on the pins that connect them, thereby preventing damage to the pins. In addition, by providing the refrigerant gas flow path facing the back of the movable scroll member, the refrigerant gas that has passed through the flow path is separated from the oil, and the separated oil sufficiently lubricates the rotation prevention mechanism. It is done.

(Effects of the Invention) As explained above, according to the present invention, the one-rotation prevention mechanism is configured by two thrust plates that face each other and a pin that connects them, so that the case and the movable scroll member are connected to each other. The acting thrust force is received by both thrust plates, reducing the thrust force acting directly on the pin, reducing pin damage and wear, and extending the life of the scroll fluid machine. .

In addition, the refrigerant gas that has passed through the flow path collides with the back surface of the movable scroll member to separate the oil, and the separated oil sufficiently lubricates the rotation prevention mechanism, allowing smooth sliding movement of the rotation prevention mechanism. It can be made into something.

[Brief explanation of the drawing]

1 to 8 relate to one embodiment of the present invention, and FIG.
The figure is a longitudinal cross-sectional view of a scroll fluid machine, Figure 2 is a cross-sectional view taken along arrows 11-11 in Figure 1 showing the main parts of the electric motor, and Figure 3 is a rn - in Figure 1 showing both thrust plates. II
4 is a partially fragmented perspective view showing the arrangement structure of both thrust plates, FIG. 5 is a side view showing the extracted pin, FIG. 6 is a perspective view of the pin, and FIG. Figure (a) is a front view showing the thrust plate, Figure 7 (b) is a cross-sectional view taken along the arrow ■-■ in Figure 7 Ca), and Figure 8 is the ■ in Figure 1 showing both scroll members. −■ It is a sectional view taken along the arrow. 3.5...Case 7...Bearing support member 13.13A...Drive shaft and crankshaft 28...
Electric motor 41.63...Movable side and fixed side scroll member 5
1...Pin 57...Flow path 58...Rotation prevention mechanism Representative Patent attorney Masaumi Mori Figure 2. Lol 3 Defense Figure 5 Figure 6 Figure 7 Figure 5a

Claims (1)

[Scope of Claims] An electric motor, a bearing support member fixed to the case and supporting the upper part of the drive shaft of the electric motor, and a crank connected to the drive shaft and eccentric to the drive shaft. a shaft; a fixed scroll member fixed to the case; a movable scroll member that is connected to the crankshaft and moves eccentrically while meshing with the fixed scroll member as the crankshaft is driven; and the movable scroll member. a rotation prevention mechanism that prevents rotation of the member; and a flow passage provided in the bearing support member that allows refrigerant gas to flow from the electric motor side to the scroll member side; an annular fixed-side thrust plate fixed to the support member; an annular movable-side thrust plate fixed to the movable-side scroll member and in surface contact with the fixed-side thrust plate; What is claimed is: 1. A scroll fluid machine, characterized in that the flow path provided in the bearing support member is provided so as to face the back surface of the movable scroll member.