JPH02211392A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To permit the smooth and quiet operation up to a high speed revolution without needing the working with high precision by installing the sliders which are fitted in slidable manners into the guide grooves on the silver guides at two positions, onto the first and second scroll members. CONSTITUTION:A crankshaft 51 which has the eccentric parts 52 and 53 at two positions and is axially supported in a housing 11, penetrating through the nearby outer diameter parts of the first and second scroll members 31 and 41, and is revolved by receiving an external driving force and drives the first and the second scroll members 31 and 41 by the eccentric parts 52 and 53 at two positions is installed. Further, slider guides 121 and 112 which have each guide groove and are positioned at two positions and axially supported in rotatable manner onto the housing and sliders 132 and 142 which are fitted in slidable manner into the guide grooves formed on the slider guides 121 and 112 at two positions on the first and second scroll members 31 and 41 are installed.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a scroll compressor, and is effective for use as a refrigerant compressor in, for example, an automobile air conditioner.

[Conventional technology and problems]

Conventionally, a scroll compressor has a movable scroll member having one or more spiral scroll teeth on a pair of disc-shaped substrates, and a fixed scroll member that are engaged with each other to form a closed working space to prevent rotation. Generally, a mechanism is used in which the movable scroll is caused to revolve around a fixed scroll member while restraining its rotation, thereby reducing the volume of the working space and performing a pumping action.

When actually operating the scroll compressor with the above configuration, the power consumption, efficiency, and durability are as follows:
The anti-rotation mechanism has a large effect, and it is important to provide balance weights at multiple locations to maintain balance against noise and vibration. As a rotation prevention mechanism for a scroll type compressor, there is a mechanism as shown in Japanese Patent Application Laid-Open No. 155916/1983. That is, in a plurality of sliding contact parts between the housing of the scroll type compressor and the movable scroll member, grooves are provided in the end faces of each, and balls or cylindrical rollers are fitted into the grooves.

However, in the anti-rotation mechanism using balls, since the rotation is prevented by point contact of the balls, the load applied to each ball is large (this means that in order to disperse the load applied to each ball, the ball is provided) It is necessary to increase the number of balls, and if the number of balls to be provided is large, the scroll teeth may slide against each other if they are large in radial direction, resulting in increased power consumption and heat generation, or the scroll teeth may The clearance between them is too large, resulting in inefficiency.For this reason, high-precision machining of the grooves is required.
It also has the problem of increased costs.

Next, regarding the balance weight, when only one of the pair of scroll members is made to revolve, it should be rotated while always maintaining a constant phase difference with the orbiting movable scroll member, as described above. It is necessary to arrange at least two balance weights. In other words, balance is achieved by three balances including the movable scroll member. However, the necessity of disposing a balance weight has problems such as an increase in the number of parts, an increase in body size and weight, and an increase in cost.

[Means to solve the problem]

A scroll compressor according to the present invention includes a first scroll member provided in a housing and having a first substrate and a first spiral tooth portion provided on one side of the first substrate; a second scroll toothed portion provided on one side of the second substrate and meshed with the first scroll toothed portion;
A scroll type compressor comprising a scroll member, having two eccentric portions, penetrating substantially outer diameter portions of the first scroll member and the second scroll member, and being pivotally supported within the housing; A shaft that rotates in response to an external driving force and drives the first scroll member and the second scroll member at the two eccentric portions, and a guide groove, and is rotatably supported by the housing. The slider includes two slider guides, and a slider that is disposed on each of the first scroll member and the second scroll member and that is slidably inserted into a guide groove disposed on the two slider guides. It is characterized by

〔Example〕

The present invention will be explained below with reference to illustrated embodiments.

FIG. 1 is a longitudinal cross-sectional view of an embodiment of a scroll compressor according to the present invention, FIG. 2 is a cross-sectional view taken along the line ■-■ in FIG.
FIG. 4 is a perspective view showing the configuration of each part. 11 is a housing, and the housing 11 includes a rotor chamber 12 and a rear side plate 13.
It is formed from. In this embodiment, the rotor chamber 1
2 and the rear plate 13 are integrally formed, and the rear plate 13 is provided with a cylindrical protrusion 15 having a ring-shaped groove 14 at the tip thereof into which the chimp seal 111 is inserted. Further, a hole 16 for rotatably supporting the slider guide 112 is provided in the rear plate 13, and a circular groove 17 for housing the O-ring 113 is formed in the hole 16. A circlip 118 prevents the slider guide 112 from coming off. Furthermore, the rear side plate 13
has a bottomed cylindrical boss portion 18, and a shaft support 114 is disposed within this boss portion 18. A ring-shaped race 115 having a notch in a portion and a thrust plate 1
16 is fixed. The race 115 has a circular groove 117
is provided. There is a suction boat in the housing 111.
(not shown) and a discharge boat 19 are each open to the outside.

Reference numeral 21 denotes a front plate, which is fixed to the housing 11 with bolts or the like (not shown). The front plate 21 is provided with a hole 22 and a circular groove 23 having the same shape as the hole 16 and the circular groove 17, and an O-ring 122 is housed in the circular groove 23. In this hole 22, the slider guide 12 is rotatably supported, and is prevented from coming off by a circlip 129. Further, a boss portion 24 is provided on the front plate 21, and a shaft support 123 and a shaft sealing device 124 are housed within the boss portion 24. Furthermore, front plate 2
1 includes the race 115 and the thrust plate 116.
A race 125 and a thrust plate 126 having the same shape are fixed to the end face facing the housing 11. The race 125 is provided with a circular groove 127 similarly to the race 115. An O-ring groove 25 is disposed around the entire circumference of the front plate 21 on the surface that contacts the housing 11, and an O-ring 128 is housed in the O-ring groove 25.

Reference numeral 31 designates a first scroll member, and a substantially spiral tooth portion 32 is provided on one side of the first scroll member 31 . The first scroll member 31 has a boss portion 33, and a bearing 131 is housed in the boss portion 33. Further, a slider 1 is provided on one side of the first scroll member 31.
32, a race 133 and a thrust plate 134 are fixed. The race 133 is provided with a circular groove 135.

Reference numeral 41 denotes a second scroll member, and on one side of the second scroll member 41, a tooth portion 42 having a substantially spiral shape that meshes with the tooth portion 32 having a substantially spiral shape of the first scroll member 31 is disposed. The tooth portion 4 has a substantially spiral shape.
A discharge port 43 is bored in the vicinity of the center of 2. Also,
The second scroll member 41 has a boss portion 44, and a bearing 141 is housed in the boss portion 44. Furthermore, a slider 142, a race 143, and a thrust plate 144 are fixed to one side of the second scroll member, and a discharge pulp 145 and a valve stopper 146 are further fixed by bolts 147.

The race 143 is provided with a circular groove 148.

51 is a crankshaft;
a first eccentric portion 52 eccentric from the axis by a predetermined amount;
A second eccentric part 53 is provided which is eccentric by the same amount of eccentricity in the opposite direction to the eccentric direction of the first eccentric part 52.

A crankshaft 51 is housed in the space formed by the housing 11 and the front plate 21, and the first scroll member 31 and the second scroll member 41 engage their substantially spiral-shaped teeth 32 and 42. It is stored in a closed state.

Here, the first scroll member 31 is supported by the first eccentric part 52 of the crankshaft 51 via a bearing 131, and the second scroll member 4 is supported by the second eccentric part 53.
1 is pivotally supported via a bearing 141. The crankshaft 51 is rotatably supported by bearings 114 and 123, and has one end protruding outside. Further, the slider 132 of the first scroll member 31 is slidably fitted into the slider guide 121 of the front plate 21, and the slider 142 of the second scroll member 41 is slidably inserted into the slider guide 121 of the front plate 21.
is slidably fitted into the slider guide 112 of the housing 11. 61 and 62 are steel balls, steel ball 61 is housed in opposing circular grooves 127 and 135 provided in races 125 and 133, respectively, and steel ball 62 is housed in opposing circular grooves 127 and 135 provided in races 115 and 143, respectively. are housed within circular grooves 117 and 148.

Next, the operation of this embodiment will be explained.

When the crankshaft 51 rotates in response to an external driving force, the first eccentric portion 52 and the second eccentric portion 53 of the crankshaft 51 perform eccentric rotational movement.

As a result, the first eccentric portion 52 and the second eccentric portion 53
, the first scroll member 31 and the second scroll member 4 are supported via bearings 131 and 141.
1 performs an eccentric movement with a phase shift of π (rad). Here, the first scroll member 31 and the second scroll member 41 move between the slider guide 121 and the slider 132, and between the slider guide 112 and the slider 14.
2 are slidably inserted into each other, this portion can only move approximately in the vertical direction in FIG. 1, and rotational movement is restricted. First scroll member 3
For convenience, such movement of the first and second scroll members 41 will be referred to as a slider crank movement.

In this slider crank movement, the farther the distance between the eccentric movement and the sliding part, the closer the movement of the moving body is to the orbital movement. However, there is a drawback that increasing the distance between the eccentric and sliding parts increases the size of the body. Therefore, in this embodiment, the positions of the parts that perform sliding motion, that is, the sliders 132 and 142, are located at the centers of the bearings 131 and 141 that undergo eccentric motion in the first scroll member 31 and the second scroll member 41, and the positions of the sliders 132 and 142 are It was decided to arrange it near the outer diameter on the opposite side to the approximate center of the toothed portion.

Next, a scroll configuration in which a pumping action is performed by a pair of moving bodies that perform slider crank movements with a phase shift of π (rad) will be described. In FIG. 5, the first scroll member 31 is shown at the lowest point of the slider crank movement, and the second scroll member 41 is shown at the highest point. When the first scroll member 31 and the second scroll member 41 perform a slider crank movement counterclockwise from this state, the solid ellipse shows an example of the locus drawn by a point on the first scroll member 31. be. The dotted ellipse is an example of the locus drawn by the points on the second scroll member 41 at this time. The toothed portion 32 is formed into an involute scroll shape, and the profile of the toothed portions 32 and 42 having a substantially spiral shape is caused by the slider crank movement.
A sealing point is created by 42 and 42, thereby forming a working chamber which is a sealed space, and this sealing point is continuously moved from the outer periphery of the tooth toward the center by the slider crank movement, and the refrigerant sucked from the outer periphery is We sought a shape that would reduce the volume of the working chamber while compressing the gas, force it to the center, and discharge it from the discharge port 43.
This is the profile of the substantially spiral tooth portion 42 of the second scroll member 41. The profile shown in FIG. 2 is one example, and the involute shape of the tooth portion 32 is corrected so that the thicknesses of the tooth portions 32 and 42 are approximately the same. In the figure, the thickness of the teeth in the left-right direction is thicker, but this is due to the characteristics of the slider crank movement.

FIG. 6 shows the compression process of the working fluid in the scroll compressor according to the present invention at the crankshaft rotation angle π/2 (
rad). The first scroll member 31 and the second scroll member 42 have the rotation center point B of the slider guide as a fulcrum, and the rotation centers C and D, which are eccentric and out of phase by π (rad) from the center point A of the crankshaft, are at A. By rotating around the point, each becomes π(
rad) Performs a staggered slider crank movement. As a result, (a) → [Yes]) → (C) → (d) → (a) →...
In this order, the working fluid moves toward the center while decreasing its volume, and compression is performed.

The slider crank movements of the first scroll member 31 and the second scroll member 41 generate forces, but the slider crank movements of the first scroll member and the second scroll member have a phase difference of π (rad). The forces generated by each component almost cancel each other out, and the deviation in the center of gravity of the first scroll member 31 and the second scroll member 41 is also small, so smooth and quiet operation is possible up to high rotations without correction by balance weights. It is possible. Therefore, a space for providing a balance weight can be omitted, which is advantageous in reducing size and weight.
3,143, thrust play) 116,126,134
, 144 and the copper balls 61, 62 do not serve as an anti-rotation mechanism, but only apply a thrust force generated in the axial direction. Therefore race 1
15. Circular grooves 117, 127, 135, 148 provided in 125, 133, 143 do not require high-precision machining, and have extremely excellent effects on improving reliability and reducing costs. It is.

Next, a second embodiment of the present invention will be described using FIG. 3. Note that the same parts as those in the first embodiment are indicated by the same numbers, and the description thereof will be omitted.

Reference numeral 82 denotes a bearing, which is fitted into a hole 26 provided approximately at the center of the front play 1/21.

Reference numeral 27 denotes an O-ring groove provided around the entire circumference of one side of the front plate 21, and an O-ring 161 is accommodated in this O-ring groove 27. A second gear 151 is fixed to one end surface of the crankshaft 51 with a bolt 152. 71 is a front cover, and a bearing 171 and a shaft sealing device 1 are installed in the boss portion 72 of the front cover 71.
72 is stored. 81 is a drive shaft, and a first gear 181 is fixed to this drive shaft 81. The front cover 71 is attached to the housing 11 and the front plate 2 by bolts (not shown) or the like.
It is fixed integrally with 1. A drive shaft 8I is housed in the space formed by the front cover 71 and the front plate 21, and the drive shaft 81 is rotatably supported by bearings 82 and 171. Further, in this state, the second gear 151 and the first gear 181 are meshed.

Next, the operation of this embodiment will be explained. In the scroll compressor of this embodiment, the drive shaft 81 is rotated by an external driving force, and the driving force is transmitted from the meshing first gear 181 to the second gear 151, thereby rotating the crankshaft 51. Since the subsequent operations are the same as those in the first embodiment, the explanation will be omitted. That is, in the case of this embodiment, the driving force is transmitted from the first gear 181 to the second gear 151, and the drive shaft 81
In contrast, the crankshaft 51 is rotated at an increased speed. In the case of this embodiment, the first gear 181 and the second gear 15
1 has a tooth ratio of 2:1, and dimensions are selected such that the center axis position of the drive shaft 81 almost coincides with the center axis position of the large outer diameter portion of the nozzing 11. As a result, compared to the scroll compressor of the first embodiment, the scroll type compressor of this embodiment can discharge by simply increasing the length in the axial direction a little without increasing the size in the radial direction. Capacity can be doubled.

In addition, when a pulley or magnetic clutch is installed to receive external driving force, the center axis of the pulley or magnetic clutch and the center axis of the part with the largest outside diameter of the compressor body as in this embodiment. If these are approximately the same, the front projected area can be made smaller than that of the first embodiment, and the mounting space can be used effectively.

Furthermore, the scroll type compressor according to the present invention has performance equivalent to that of scroll type compressors generally used at present in terms of compression work efficiency, suction and discharge pulsations, etc. In addition to the above-mentioned features, it has an extremely excellent feature of having the above-mentioned technical effects.

〔Effect of the invention〕

As described above, the present invention has technical effects equivalent to those of conventionally used scroll compressors in terms of compression efficiency and suction/discharge pulsation, and also does not require high-precision machining of the anti-rotation mechanism. A scroll compressor that can operate smoothly and quietly up to high rotation speeds without requiring balance correction using a balance weight can be obtained.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view showing the first embodiment of the present invention, FIG. 2 is a cross-sectional view taken along the line ■-■ in FIG. 1, and FIG.
FIG. 4 is a longitudinal cross-sectional view showing an embodiment of the present invention, FIG. 4 is a perspective view showing the structure of the first scroll member, second scroll member, slider guide, crankshaft, and steel ball of the first embodiment of the present invention, and FIG. 5 is a slider First to explain crank motion
FIG. 3 is a diagram schematically showing a scroll member and a second scroll member. FIGS. 6(a) to 6(d) are diagrams showing the compression process of working fluid in the scroll compressor according to the present invention for each crankshaft rotation angle π/2 (rad). 31... First scroll member, 41... Second scroll member, 51... Crankshaft, 112, 12
1...Slider guide agent patent attorney Takashi Okabe (one idiot) Figure Figure

Claims (1)

[Claims] 1. a first scroll member provided in the housing and having a first substrate and a spiral first scroll tooth provided on one side of the first substrate; a second scroll member having a spiral second scroll tooth provided on one side of the second substrate and meshing with the first scroll tooth; and a second scroll member having two eccentric portions, and having a shaft in the housing. supported,
In a scroll compressor comprising a shaft that rotates in response to an external driving force, the shaft passes through substantially outer diameter portions of the first scroll member and the second scroll member, and the shaft rotates at the two eccentric portions. two slider guides that drive the scroll member and the second scroll member and have guide grooves at one end and are rotatably supported by the housing; 1. A scroll compressor comprising: a slider which is arranged and slidably inserted into the guide grooves of the two slider guides.