JPS6364632B2 - - Google Patents

Description

[Detailed description of the invention]

The present invention relates to a oscillating swash plate compressor, and more particularly to a oscillating swash plate compressor that is smaller in size, lighter in weight, and has lower vibration and noise than conventional compressors. A typical conventional oscillating swash plate compressor has a structure as shown in Figure 1.The main shaft and cylinder are arranged parallel to each other, making it compact overall, and is commonly used in vehicle-mounted compressors. However, various problems arose. First, the structure and shortcomings of the conventional oscillating swash plate compressor will be explained. In Fig. 1, 1 is a Z-type crankshaft, which is connected to an electric motor (not shown) and transmits rotational motion as indicated by arrow A. do. 1′,
1'' is a journal part of the Z type crankshaft, 2 and 2' are crank arms, which are connected at an angle with respect to the center axis of the Z type crankshaft 1 as shown in the figure. 3 is a crank pin, which is connected to the crankshaft 1. It is connected perpendicularly to the arms 2 and 2'. 4 is an oscillator, and the crank pin 3 passes through a hole passing through the center of the oscillator.
The crank arms 2 and 2' are supported by contact surfaces with the crank pin 3, and are structured to slide on the contact surfaces during operation. The oscillator 4 has arms 4a, 4
b extends left and right, and piston rods 6a, 6b
The pistons 5a and 5b are connected via. 1
0a and 10b are cylinders housing pistons 5a and 5b, respectively. In order to prevent the rocker 4 from rotating together with the rotation of the Z-type crankshaft 1, the tips of its arms 4a and 4b are provided with guides 7a,
It is designed to slide on this along line 7b.
In addition, the arms 4a and 4b of the oscillator 4 and the piston rod 6
The connection points with a and 6b are ball joints 8a and 8
It is connected by b. This means that this connection point not only moves horizontally and vertically within a plane that includes the connecting rods 6a and 6b, but also moves the arm 4 of the oscillator 4.
This is because a and 4b move as shown by arrow B around the axis of the arm. Further, the connection points between the piston rods 6a, 6b and the pistons 5a, 5b are also connected using ball joints 9a, 9b, and the ball joints 9a, 9b are connected to the cylinders 10a, 10b.
If there are two arms 4a and 4b of the oscillator 4, a pin joint may be used. In a conventional oscillating swash plate compressor having such a structure, the structure of the connection point between the oscillator 4 and the piston rods 6a and 6b is a ball joint 8 as shown in FIG.
Since the pistons 5a and 8b are used, the pistons 5a and 5b cannot be of opposed type. Therefore, the force is unbalanced and vibrations are likely to occur. For this reason, high-speed operation is not possible, and the size and weight increase. Compared to other types of compressors with the same throughput, the capacity of each piston is larger, so the overall width is wider, making it impossible to store it in a long and narrow space such as under the floor of a train. In addition, the oscillator 4 and guides 7a, 7
The oscillation speed with b is fast, which increases wear and heat generation of the sliding parts, making it impossible to operate at high speeds when the size is large. Furthermore, joints 8a, 8b,
As shown in 9a and 9b, many joints are required, which causes high cost and low reliability. In view of the above drawbacks of the conventional rocking swash plate type compressor, the present invention uses opposed pistons, gives the cylinder the role of a guide, making it unnecessary, and reduces the number of joints, resulting in a smaller size. ,Weight saving,
This invention relates to a oscillating swash plate compressor that achieves low vibration, low noise, high reliability, and low cost. The present invention will be explained in detail below using examples. First, the first embodiment shown in FIGS. 2 and 3 will be explained. In FIG. FIG. 3 is a cross-sectional front view of an oscillating compressor having an oscillating type compressor, and FIG. 3 is a side view of an oscillator and a ball joint of the compressor of FIG. 2. In the figure, 1 is a Z-type crankshaft, 1', 1'' are its journal parts, 2, 2' are crank arms, 3 is a crank pin, 14 is an oscillator, and 14a, 14b are the arms of the oscillator. 15a, 15b and 15c, 15d are respectively Z.
These pistons are arranged around the type crankshaft 1, and the pistons 15a and 15b are arranged opposite to each other with the central axis coaxial.
a, 16b. The piston rods 16a and 16b are connected to each other via a double sliding ball joint 11a. Another pair of pistons 15c and 15d are arranged on the same plane as the pistons 15a and 15b, and at symmetrical positions with respect to the center axis of the Z-shaped crankshaft 1. Piston rods 16c, 16 are disposed at opposite positions with the pistons 15c, 15d coaxial with each other.
d, and the piston rods 16c, 16d are connected via a double sliding ball joint 11b, as in the case of the piston rods 16a, 16b. Each piston 15a, 15b, 15c, 15d is a cylinder 20a, 20b, 20 coaxial with the central axis, respectively.
It is stored in c, 20d. each cylinder 20
A, 20b, 20c, and 20d are each provided with a gas suction valve and a gas discharge valve, and each piston 15
Gas is sucked into the cylinders 20a, 20b, 20c, and 20d, compressed, and discharged by the operation of the cylinders a, 15b, 15c, and 15d. The double sliding ball joints 11a and 11b move in three dimensions within the ball support member 21 by sliding between them and the support surface of the support member 21. Furthermore, the ball 22 has a through hole 23 passing through its center, and the arm 14a or 14b of the rocker 14 passes through the through hole 23. Note that the configurations of the crank arms 2, 2', crank pin 3, and rocker 4 are not limited to those shown in FIG. 2, but may be any so-called rocking swash plate type compressor. Therefore, a Z-type crankshaft shown in FIG. 4 may be used. Next, the operating state of the compressor of this embodiment will be explained. As the Z-type crankshaft 1 rotates in the direction of arrow A, the crank arms 2, 2' and crank pin 3 also rotate in the same direction. The oscillator 14 is supported by the contact surfaces with the crank arms 2, 2' and the crank 3, and slides on the contact surfaces, so that the oscillator arm 14a
and 14b is rocked left and right. Further, the accompanying vertical movement of the oscillator arms 14a, 14b relative to the ball joints 11a, 11b is caused by the movement of the oscillator arms 14a, 14b through the through hole 23, as described above.
14b, and the rocker arm 14
The movement of a and 14b in the direction of the arrow B also occurs in the through hole 2.
3 Sliding to the inner wall or ball joint 11a,
11b is absorbed by sliding with the ball joint support member 21. In this way, Z type crankshaft 1
The rotational motion of the piston rods 16a, 16b, 16c, and 16d is converted into horizontal movement of the piston rods 16a, 16b, 16c, and 16d, which causes the pistons 15a, 15b, 15c, and 15d to move left and right within the cylinders 20a, 20b, 20c, and 20d, thereby moving the piston rods 16a, 16b, 16c, and 16d left and right. Gas is inhaled, compressed, and exhaled. At this time, the rocker arms 14a, 14b
tries to rotate in the direction of rotation of the main shaft (direction of arrow A), but the force in this direction is exerted by the ball joint 11.
a, 11b and piston rods 16a, 16b, 1
Each piston 15a, 15 via 6c, 16d
b, 15c, and 15d, and is supported by each piston and the inner wall of each cylinder 10a, 10b, 10c, and 10d. That is, in the case of the compressor of the present invention, the walls of each cylinder play the role of the guides 7a, 7b of the conventional oscillating swash plate type compressor. Therefore, the force of rotation in the direction of arrow A is distributed to each piston, resulting in a smaller load than on the guides 7a and 7b. Furthermore, since the sliding distance is shorter and slower than that in the guides 7a and 7b, less heat generation and wear occur. Therefore, the cylinder 20b and the piston 15b do not necessarily have to be a cylinder and a piston, but may be a guide cylinder and a cross guide. Similarly, the cylinder 20d and the piston 15d may also be a guide tube and a cross guide. In other words, by making the cylinders face each other or by arranging the cylinders and guide tubes facing each other, it is possible to reduce the heat generation and wear caused by the sliding of the guide part, which is a drawback of conventional oscillating swash plate compressors. It becomes possible to do so. Next, a second embodiment of the present invention will be described. In this embodiment, a pair of cylinders arranged opposite to each other are
This is an example where four sets are arranged around the molded crankshaft 1. That is, FIG. 5 is a cross-sectional front view when there are eight cylinders, FIG. 6 is a side view of the center of the rocker and joint part of the rocking swash plate compressor of FIG. 5, and FIG.
The figure is a view of the double sliding pin joint used in the compressor of FIG. In the figure, the Z-type crankshaft 1, its journal parts 1', 1'', crank arms 2, 2', and crank pin 3 are the same as in the previous embodiment. However, the oscillator 24 is as shown in FIG. Four rocker arms 24a, 24b, 24
c, 24d. Also, the piston is
In addition to 5a, 15b, 15c, and 15d (not shown), there are also 15e, 15f, 15g, and 15h, and the piston rods are also similar to those 16a, 16b, 16c, and 16.
In addition to d (not shown), 16e, 16f, 16g,
16h, and the cylinders are also 20a, 20b,
In addition to 20c and 20d (not shown), 20e and 20
There are f, 20g, and 20h. Also in the case of this embodiment, the oscillators 24a, 24b and the double sliding type joints 11a, 11 attached to their tips
b movement, and the accompanying piston rod 16a, 1
Movement of 6b, 16c, 16d, each piston 15
The movements of a, 15b, 15c, and 15d are exactly the same as in the previous embodiment. However, since the rocker arms 24c and 24d move differently from those of the rocker arms 14a and 14b in the above embodiment, the joints connecting these and each piston are shown in FIG. 7, unlike the double sliding ball joints described above. A double sliding pin joint is used. This is because the tips of the oscillator arms 24c and 24d rotate as the Z-type crankshaft 1 rotates in the direction of arrow A.
As shown in Fig. 5, in addition to the movement in the left-right direction, the up-down direction, and the direction of arrow B (twisting movement), there is also the movement in the up-down direction in Fig. 7 (movement in the rotational direction of the Z-type crankshaft 1 in Fig. 5). This is because it accompanies Therefore, in the case of this embodiment, the double sliding pin joints 12a and 12b are connected to the rocker arm 2 as shown in FIG.
In order to absorb the vertical movement of 4c and 24d in FIG. 7, the length of the pin is increased to provide a gap a. Joints 12a and 12b with such structure
Due to the provision of
piston rods 16e, 16 via c, 24d
f, 16g, 16h, piston 15
Operate e, 15f, 15g, and 15h smoothly. In this embodiment, the structure is such that four sets of cylinders are provided around the Z-type crankshaft 1, and the joint between the rocker arm and the piston rod is a double sliding ball joint with two joints in the same plane. The other two ball joints are double sliding pin joints with a gap a like the one above, but the above two double sliding ball joints can also be double sliding pin joints without a gap a. good. That is, any joint having a structure that prevents movement of the oscillator arm in the rotational direction of the Z-type crankshaft may be used. Furthermore, for the same reason, the number does not need to be two, but only one. Furthermore, the number of cylinder groups arranged around the Z-type crankshaft 1 is not limited to four (eight), and it goes without saying that any number of groups may be used. When we manufactured and operated a helium compressor with the structure of this example and the specifications shown in the table below, it showed the expected performance against vibration and noise, and also confirmed test items such as high speed and continuous operation. Very good results have also been obtained.

[Table] The present invention has the structure and operates as described above, and its features and effects are as follows. Namely, (i) the cylinder and piston were made to face each other and were arranged symmetrically, resulting in a better balance of forces and less vibration and noise. (ii) Due to the structure that does not require the rocker arm guide and the reason mentioned in (i) above, high-speed operation is possible. (iii) The ability to operate at high speeds has made it possible to make the compressor smaller and lighter than other compressors of the same capacity. (iv) For the same reason, it has become possible to manufacture a compressor with a large throughput compared to other types of compressors with similar volumes. (v) By making the cylinders face-to-face, it became possible to manufacture a long and narrow compressor suitable for mounting on vehicles. (vi) By reducing the number of joints and contact sliding parts, the factors contributing to high costs and decreased reliability are reduced. Because of these characteristics, it is especially suitable as a helium gas compressor to be mounted on a car rather than magnetic levitation.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional front view showing a conventional oscillating swash plate compressor, FIG. 2 is a sectional front view showing an embodiment of the oscillating compressor of the present invention, and FIG. 3 is a compressor shown in FIG. A side view of the rocker and ball joint of the machine, FIG. 4 is a sectional front view showing another Z-shaped flank shaft, FIG. 5 is a sectional front view showing another embodiment, and FIG. FIG. 7 is a side view of the central part of the rocker and joint portion of the compressor, and FIG. 7 is a view taken along the - arrow in FIG. 1 is a Z type crank, 3 is a crank pin, 11
a, 11b are double sliding ball joints, 12
a, 12b are double sliding pin joints, 14,
24 is an oscillator, 14a, 14b, 24a to 24
d is the arm, 15a to 15h are the pistons, 16
a to 16h are piston rods, 20a to 20
h is a cylinder.

Claims (1)

[Claims] 1. At least two pairs of cylinders and cylinders or guide tubes arranged in parallel with each other and coaxial with each other and housed in the cylinders or guide tubes. At least two sets of pistons and pistons or cross guides, a piston rod connecting the pistons or the pistons and the cross guide, a double sliding joint provided in the middle thereof, and the at least two sets of cylinders. A Z-type crankshaft is arranged in parallel between a pair of cylinders or a pair of cylinders and a cross guide, and a crank pin of the Z-type crankshaft passes through the center thereof, and the number of pairs of cylinders or cylinders and cross guides is A rocking slope comprising a rocker having a number of arms opposite to each other, the arms of the rocker being connected to a double sliding joint provided in the middle of each of the piston rods. Plate compressor. 2. In the oscillating swash plate compressor according to claim 1, one or two of the double sliding joints provided in the middle of the piston rod are connected to the oscillator arm. A rocking swash plate type compressor, characterized in that the joint is structured to prevent rotational movement of the Z-type crankshaft. 3. The oscillating swash plate compressor according to claim 2, wherein the double sliding joint is a double sliding ball joint. .