JPH10141217A - Multiple reciprocating pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress fluctuation of discharging pressure by setting a crank pin position so as to arrange a rotary angle of a peak discharging flow rate time of each reciprocat ing pump in parallel with a rotary angle of a driving shaft at equal intervals following with each operating order, in a plurality of reciprocating pump. SOLUTION: Crank arm center lines 100, 102, 104, 106, 108 are respectively crank arm center lines of crank arm 40 for #1 to #5 uniflow piston pumps 34. When the crank arm center lines 100, 108, 102, 104, 106 are set at the angular interval of 72 deg., the peak discharge flow rate time of #2 and #4 pumps is deviated from the 72 deg. interval. The rotary angle at the time of peak discharge flow rates are arranged each other at the 72 deg. interval. The crank arm center lines 102, 106 of a crank arm 40 for the unifolow piston pumps 34 of a low stage group 72 are therefore set at the angular interval of 44 deg. with respect to the crank arm center lines 108, 104 of the crank arm 40 for the uniflow piston pumps 34 whose operating order is just before in the turning direction of the crank shaft 12. Accordingly the turning angle of each uniflow piston pump 34 at the peak discharge flow rate time is arranged on the turning angle of the crank shaft 12 at the angular interval of 72 deg. according to the operating order.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multiple reciprocating pump device, and more particularly to a multiple reciprocating pump device having a plurality of reciprocating pumps in a plurality of stages to reduce the overall size. .

[0002]

2. Description of the Related Art Japanese Patent Application Laid-Open No. 52-59304 discloses a multiple reciprocating pump in which a plurality of reciprocating pumps driven by a common drive shaft are divided into two groups having different stages while keeping their center lines parallel to each other. A pump device is disclosed. Such a multiple reciprocating pump device has an advantage that the entire reciprocating pump device can be reduced in size as compared with a multiple reciprocating pump device in which reciprocating pumps are arranged in one stage. In such a conventional multiple reciprocating pump device, the crankpin positions of the reciprocating pumps are arranged at equal angular intervals on the rotation angle of the drive shaft.

[0003]

Since the positions of the crank pins of the reciprocating pumps are arranged at equal angular intervals on the rotation angle of the drive shaft, the rotation of the peak discharge flow rate of each reciprocating pump on the rotation angle of the drive shaft. The angles are not equiangularly spaced, and the discharge flow rate is significantly increased at a predetermined rotation angle. As a result, the fluctuation of the discharge pressure at the common discharge port of the multiple reciprocating pump device is large.

[0004] An object of the present invention is to achieve downsizing.
An object of the present invention is to suppress the fluctuation of the discharge pressure in a multiple reciprocating pump device provided in a plurality of stages without a plurality of reciprocating pumps being arranged in a line.

[0005]

According to the multiple reciprocating pump device (10) on which the present invention is based, each reciprocating pump (34) is
A reciprocating member (36) that discharges fluid from the pump chamber (58) to a common discharge port (66) and increases or decreases the volume of the pump chamber (58) by reciprocating motion is connected to a connecting rod.
It is connected to a common drive shaft (12) via (42). Each reciprocating pump (34) has the reciprocating direction of the reciprocating member (36) substantially the same, and is substantially perpendicular to both the reciprocating direction of the reciprocating member (36) and the axial direction of the drive shaft (12). It is arranged in a plurality of groups in different directions. And in such a multiple reciprocating pump device (10), a plurality of reciprocating pumps (34)
The crank pin position (82) is set so that the rotation angles of the reciprocating pumps (34) at the peak discharge flow rate (90) are arranged at equal angular intervals on the rotation angle of the drive shaft (12) according to their operation order. ing.

The drive shaft (12) of the multiple reciprocating pump device (10) includes not only a crankshaft but also a drive shaft (12) having an eccentric circular cam into which the large end of the connecting rod (42) is fitted. Include.

At the time of peak discharge flow rate from each reciprocating pump (34)
The rotation angles of (90) are arranged at equal angular intervals above the rotation angle of the drive shaft (12). Thereby, the entire peak and bottom of the multiple reciprocating pump device (10) are dispersed, and the pressure fluctuation of the discharge port (66) of the multiple reciprocating pump device (10) is suppressed.

According to another multiple reciprocating pump device (10) of the present invention, the reciprocating pump (34) is provided with a reciprocating member (36) when the connecting rod (42) moves toward the reciprocating pump (34). First and second two groups (70, 7) in which the angle with respect to the reciprocating direction is a first angle and a second angle larger than the first angle, respectively.
The number of reciprocating pumps (34) in the first group (70) is larger than the number of reciprocating pumps (34) in the second group (72).

Each connecting rod (42) approaches the reciprocating pump (34) in one half rotation of the drive shaft (12) and separates from the reciprocating pump (34) in the other half rotation. Connecting rod
During the period when (42) approaches the reciprocating pump (34), the drive shaft
(12) receives a large load from the connecting rod (42). Then, the connecting rod (4) in the reciprocating direction of the reciprocating member (36).
The larger the angle of 2), the more the connecting shaft (1)
The load on 2) increases. The first angle is less than the second angle and the second group (72) of uniflow piston pumps.
The number of 34 is the uniflow piston pump 34 of the first group (70).
As a result, the drive shaft (12)
The number of times a large load is applied from (42) is suppressed, and the drive shaft (1
This can lead to improvement of durability of 2).

According to another multiple reciprocating pump apparatus (10) of the present invention, the total number of reciprocating pumps (34) is n,
(34) is divided into two groups (70,72), one of which (7
The crank pin position (82) of the reciprocating pump (34) of (0) is
The rotation angle of 360 ° / n or a multiple of 360 ° / n above the rotation angle of 2), and the position of the crankpin of the reciprocating pump (34) of the other group (72)
(82) is the reciprocating pump (34) of one group (70) in which the rotation angle at the peak discharge flow rate (90) of the reciprocating pump (34) of the other group (72) is one before in the operation order. At peak discharge flow rate of 34)
The rotation angle of the drive shaft (12) is set to be 360 ° / n above the rotation angle of (90).

A reciprocating member (36) of a reciprocating pump (34) having the same group.
Then, the connecting rod for the reciprocating direction of the reciprocating pump (34)
The angle change in (42) is shifted by the angular interval at (90) at the peak discharge flow rate. Therefore, by moving the crank pin position (82) of the reciprocating member (36) of the reciprocating pumps (34) of the same group apart by 360 ° / n or a multiple thereof on the rotation angle of the drive shaft (12), these reciprocating pumps The rotation angle at the peak discharge flow rate (90) in (34) is also shifted by the same amount. Reciprocating pump of the other group (72)
The rotation angle at the peak discharge flow rate (90) of (34) is changed to the peak discharge flow rate (90) of the reciprocating pump (34) of the other group (72) which is operated immediately before the reciprocating pump (34). If the crank pin position (82) of the reciprocating pump (34) of the other group (72) is set to be 360 ° / n apart from the reciprocating pump (34) in the entire multiple reciprocating pump device (10). The rotation angles at the time (90) of the peak discharge flow rate can be arranged at equal angular intervals.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the drawings. 5 is a vertical sectional view of the two-stage five-piston piston pump device 10 as viewed from the axial direction of the crankshaft 12, and FIG. 6 is a partial cross-section of the two-stage five-piston piston pump device 10 as viewed from the left in FIG. FIG. 7 is a partially sectional view of the two-stage five-piston piston pump device 10 as viewed from above. This two-stage five-piston piston pump device 10 is provided in a washing machine, a chemical sprayer, or the like. The crankshaft 12 extends in the horizontal direction, and is rotatable by roller bearings 16 at both ends.
It is pivotally supported by 14 side walls. On the tip side of the crankcase 14, the suction side distribution pipe 18, in order from the crankcase 14,
A cylinder pipe 19 and a discharge manifold 20 are provided.
The studs 22, 24 are partially embedded in the crankcase 14, the nut 26 is screwed into the tip of the stud 24, and the suction side distribution pipe 18 is fastened to the crankcase 14,
Join. The nut 28 is screwed into a male screw portion provided at the tip of the nut 26, and the discharge manifold 20 is tightened toward the crankcase 14, and the cylinder pipe 19 and the discharge manifold 20 are respectively connected to the suction side distribution pipe 18 and the cylinder pipe. Join to 19. The suction pipe 30 is connected to a lower portion of the suction side distribution pipe 18 and has a suction port 32 at a lower end.

The two-stage five-piston piston pump device 10 includes:
The five uniflow piston pumps 34 are provided in a staggered arrangement (FIG. 6) with their longitudinal directions aligned in the horizontal direction and viewed from the discharge manifold 20 side. FIG. 4 shows the arrangement and numbers of the uniflow piston pump 34 when the two-stage five-piston piston pump device 10 is viewed from the distal end side. Numbers # 1, # 2, # 3, # 4, and # 5 are sequentially numbered from one end (the left end in FIG. 4) in the axial direction of the crankcase 14. The # 1, # 3, and # 5 uniflow piston pumps 34 belong to the upper group 70, and the # 2 and # 4 uniflow piston pumps 34 belong to the lower group 72. Lower group 72
Of the two uniflow piston pumps 34 are located at the center of the horizontal center of the cross section of the three uniflow piston pumps 34 of the upper group 70 in the horizontal direction. In the two-stage five-piston piston pump device 10, the operation order of the uniflow piston pumps 34 is # 1, # 5, # 2, # 3
It is set to # 4.

In each uniflow piston pump 34,
The piston rod 36 extends in a horizontal direction perpendicular to the horizontal direction of the crankshaft 12, and has a rod portion 37 and a crosshead 38 to which the base end of the rod portion 37 is screwed. The connecting rod 42 is rotatably fitted to the crank arm 40 of the crankshaft 12 at the large end, and is cross-headed by the pin 44 at the small end.
It is rotatably connected to 38. The crosshead 38 is inserted into a cylindrical guide portion 46 of the crankcase 14, and is guided in the axial direction of the piston rod 36 by the guide portion 46. The oil seal 48 is fitted and fixed to the distal end portion of the guide portion 46 with its axial position fixed, and slides in contact with the rod portion 37 of the piston rod 36 on the inner peripheral side. Prevent leakage of lubricating oil. The valve seat 50 and the stopper 52 with the through-hole are spaced apart in the axial direction of the piston rod 36 so that the stopper 52 with the through-hole is located on the distal end side of the valve seat 50.
Is fixed to the tip of the. The valve element 54 is loosely fitted to the rod portion 37 between the valve seat 50 and the stopper 52 with the through-hole, and the piston packing 56 is fitted to the outer peripheral side of the valve element 54 and slides on the inner periphery of the cylinder pipe 19. The pump chamber 58 is formed in the cylinder pipe 19 on the tip side of the piston rod 36. Seal packing 60
Is disposed at the junction between the crankcase 14 and the suction-side distribution pipe 18, slides on the inner peripheral side of the rod portion 37 of the piston rod 36, and the suction liquid flows from the suction-side distribution pipe 18 toward the crankcase 14. To prevent leakage. Pump chamber 58 is discharge manifold 20
It communicates with the upper part of the discharge manifold 20 via a passage 62 inside. A discharge valve 64 is provided for each pump chamber 58,
Arranged at the upper end of each pump chamber 58, it allows one-way liquid flow from each pump chamber 58 to a discharge port 66 common to all the uniflow piston pumps 34.

FIG. 2 shows the rotation angle of the crankshaft 12 and the piston rod of the uniflow piston pump 34 in the upper group 70 and the lower group 72.
36 shows the relationship between the top dead center position (solid line) and the bottom dead center position (two-dot chain line). R indicates the rotation direction of the crankshaft 12. The four crank pin positions 82 shown are the crank pin positions Ut and Ub of the top dead center and the bottom dead center of the uniflow piston pump 34 of the upper group 70, respectively, and the lower group
The crankpin positions Dt and Db at the top dead center and the bottom dead center of the 72 uniflow piston pump 34 are shown. Crank pin position
The reference numeral 82 moves on a circumference having a diameter L about the center O of the crankshaft 12. The upper pump center line 86 and the lower pump center line 88 of the uniflow piston pump 34 of the upper group 70 and the lower group 72 are parallel to a reference horizontal line 84 passing through the center O of the crankshaft 12, and are mutually H1 in the vertical direction. Just away. The reference horizontal line 84 is at the center of the interval between the upper pump center line 86 and the lower pump center line 88. The offset amount of the upper pump center line 86 and the lower pump center line 88 with respect to the reference horizontal line 84 is H2 (= H1 / 2). Has become. Piston rod 36
Is larger than L (L1> L). The rotation angle range θ1 of the crankshaft 12 from the bottom dead center to the top dead center of the piston rod 36 of the uniflow piston pump 34 in the upper group 70
Is that the piston rod 36 of the uniflow piston pump 34 of the lower group 72 is larger than the rotation angle range θ2 of the crankshaft 12 from the bottom dead center to the top dead center (θ1> θ2). As described above, since the crankpin positions 82 at the bottom dead center and the top dead center of the piston rod 36 of each uniflow piston pump 34 are not exactly opposite to O, the crankpin positions 82 of all the uniflow piston pumps 34 are changed. Due to the rotation angle of the crankshaft 12,
Even if arranged at equal angular intervals, all uniflow piston pumps 34
The lower dead center, the upper dead center, and the peak discharge flow rate 90 (FIG. 3) are not at equal angular intervals due to the rotation angle of the crankshaft 12.

The crankshaft 12 approaches the uniflow piston pump 34 in the vertical direction by a half rotation of the upper group 70 side,
In the vertical direction half-turn on the lower group 72 side, it separates from the uniflow piston pump. Accordingly, the angle of the connecting rod 42 with respect to the reference horizontal line 84 during the compression stroke is such that the connecting rod 42 of the uniflow piston pump 34 of the upper group 70 is
Is smaller than the connecting rod of the uniflow piston pump. During the compression stroke, the crankshaft 12
The greater the load is received from the reference rod 42 and the greater the angle of the connecting rod 42 with respect to the reference horizontal line 84 during the compression stroke, the greater the load received. Since the number of the uniflow piston pumps 34 in the lower group 72 is smaller than the number of the uniflow piston pumps 34 in the upper group 70, the load on the crankshaft 12 is suppressed.

FIG. 3 shows the rotation angle of the uniflow piston pump 34 at the peak discharge flow rate 90 when the crankpin positions 82 of the uniflow piston pumps 34 are arranged at equal angular intervals above the rotation angle of the crankshaft 12. I have. In FIG.
1, 2, 3, 4, and 5 mean the # 1, # 2, # 3, # 4, and # 5 uniflow piston pumps 34, respectively. The crankpin positions 82 of each uniflow piston pump 34 are arranged in accordance with the operation order. # 1 uniflow piston pump 34
When the rotation angle of the crankpin position 82 of the # 1 is set to 0 °, the # belongs to the same upper group 70 as the # 1 uniflow piston pump 34.
The crank pin position 82 of the # 3, # 5 uniflow piston pump 34 has a rotation angle of 72 ° or a multiple thereof. On the other hand, the rotation angle of the crankpin position 82 of the uniflow piston pump 34 belonging to the lower group 72 deviates from a multiple of 72 ° for the reason described in FIG. Although these shift amounts are related to the offset amount H2, FIG.
The deviation amount of # 2 and # 4 from the rotation angle of 2 ° or a multiple thereof is 28 ° toward the delay side.

FIG. 1 shows the uniflow piston pumps 34 so that the rotation angles of the uniflow piston pumps 34 at the peak discharge flow rate 90 are equal angular intervals above the rotation angle of the crankshaft 12.
3 shows the angular interval between the center lines of the crank arms 40 of the crank shaft 12 when the crank pin position 82 is set.
Crank arm center lines 100, 102, 104, 106, and 108 are the crank arm center lines of the crank arms 40 for the # 1, # 2, # 3, # 4, and # 5 uniflow piston pumps 34, respectively. Lines 100, 108, 102, 104,
If 106 is set at intervals of 72 °, the rotation angle of 90 at the peak discharge flow rate is shifted from the 72 ° interval at the peak discharge flow rates of # 2 and # 4 as described in FIG.
The crank arm centerlines 102 and 106 of the crank arm 40 for the uniflow piston pump 34 in the lower group 72 are arranged one by one in the rotation direction of the crankshaft 12 so that the rotation angles of 90 are arranged at intervals of 72 °. Crank arm centerline 10 of crank arm 40 for front uniflow piston pump 34
The interval is set to 44 ° with respect to 8,104.
As a result, the rotation angle of each uniflow piston pump 34 at the peak discharge flow rate 90 is changed according to the operation order.
Are arranged at regular intervals of 72 ° above the rotation angle of. As a result, the liquid discharged from each of the uniflow piston pumps 34 is uniformly dispersed and supplied to the discharge port 60 of the two-stage five-piston piston pump device 10, so that the fluid pressure fluctuation of the discharge port 60 is reduced.

[Brief description of the drawings]

FIG. 1 shows each crank arm of a crankshaft when the position of the crankpin of each uniflow piston pump is set so that the rotation angles at the peak discharge flow rate of each uniflow piston pump are equal angular intervals above the rotation angle of the crankshaft. FIG. 5 is a diagram showing an angular interval of a center line of FIG.

FIG. 2 is a diagram showing the relationship between the rotational angle of a crankshaft and the top dead center position (solid line) and the bottom dead center position (two-dot chain line) of the piston rods of the upper and lower group uniflow piston pumps.

FIG. 3 is a diagram showing a rotation angle at a peak discharge flow rate of each uniflow piston pump when crank pin positions of each uniflow piston pump are arranged at equal angular intervals on a rotation angle of a crankshaft.

FIG. 4 is a view showing the arrangement and numbers of the uniflow piston pump when the two-stage five-piston piston pump device is viewed from the distal end side.

FIG. 5 is a vertical cross-sectional view of the two-stage five-piston pump device as viewed from an axial direction of a crankshaft.

FIG. 6 is a partial cross-sectional view of the two-stage five-piston piston pump device as viewed from the left in FIG. 5;

FIG. 7 is a partially sectional view of the two-stage five-piston piston pump device as viewed from above.

[Description of Signs] 10 Two-stage five-piston pump device (multiple reciprocating pump device) 12 Crankshaft (drive shaft) 34 Uniflow piston pump (reciprocating pump) 36 Piston rod (reciprocating member) 42 Connecting rod 58 Pump chamber 66 Discharge port 70 Upper group (first group, one group) 72 Lower group (second group, other group) 82 Crank pin position 90 At peak discharge flow rate

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[Procedure amendment]

[Submission date] March 21, 1997

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0012

[Correction method] Change

[Correction contents]

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the drawings. 5 is a vertical cross-sectional view of the two-stage five-piston piston pump device 10 as viewed from the axial direction of the crankshaft 12, and FIG. 6 is a partial cross-section of the two-stage five-piston piston pump device 10 as viewed from the left in FIG. FIG. 7 is a partial sectional view of the two-stage five-piston pump device 10 as viewed from above. The two-stage five-piston piston pump device 10 is provided in a washer, a chemical sprayer, and the like. The crankshaft 12 extends in the horizontal direction,
Both ends are rotatably supported by roller bearings 16 on the side walls of the crankcase 14. A suction side distribution pipe 18, a cylinder pipe 19, and a discharge manifold 20 are arranged at the tip end side of the crankcase 14 in order from the crankcase 14. Stud side 2 of stud
2, rare embed the crankcase 14, nut 26
Is screwed into the tip portion 24 of the stud, and the suction side distribution pipe 18 is fastened to the crankcase 14 and joined thereto.
The nut 28 is screwed into a male thread provided at the tip of the nut 26, and the discharge manifold 20 is tightened toward the crankcase 14, and the cylinder pipe 19 and the discharge manifold 20 are respectively connected to the suction side distribution pipe 18 and the cylinder pipe. 1
9 is joined. The suction pipe 30 is connected to a lower portion of the suction side distribution pipe 18 and has a suction port 32 at a lower end.

Claims (3)

[Claims] 1. A reciprocating pump (34) has a pump chamber (58).
And a reciprocating member (36) for increasing or decreasing the volume of the pump chamber (58) by reciprocating motion through a connecting rod (42). And the reciprocating pumps (34) are arranged so that the reciprocating directions of the reciprocating members (36) are substantially the same,
And the reciprocating direction of the reciprocating member (36) and the drive shaft (1
2) In the multiple reciprocating pump device (10) arranged in a plurality of groups in a direction substantially perpendicular to both of the axial directions, the plurality of reciprocating pumps (34) are arranged according to their operation order. The crank pin position (82) is set so that the rotation angles of the reciprocating pumps (34) at the peak discharge flow rate (90) are arranged at equal angular intervals on the rotation angle of the drive shaft (12). A multiple reciprocating pump device characterized by the above-mentioned. 2. The reciprocating pump (34) is connected to the connecting rod.
When (42) moves toward the reciprocating pump (34), the first angle of the reciprocating member (36) with respect to the reciprocating direction becomes a second angle larger than the first angle and the first angle. And the number of reciprocating pumps (34) of the first group (70) is divided into two groups (70, 72).
2. The multiple reciprocating pump device according to claim 1, wherein the number is larger than the number of the pumps. 3. The total number of said reciprocating pumps (34) is n,
The reciprocating pump (34) is divided into two groups (70, 72), and the crankpin position of the reciprocating pump (34) in one group (70) is
(82) has a rotation angle of 360 ° / n or a multiple thereof on the rotation angle of the drive shaft (12), and the reciprocating pump (34) of the other group (72)
The crank pin position (82) of one of the groups (70) is such that the rotation angle at the peak discharge flow rate (90) of the reciprocating pump (34) of the other group (72) is one position earlier in the operation order. Reciprocating Pump (34)
3. The multiple reciprocating method according to claim 1, wherein the rotation angle is set to be 360 ° / n above the rotation angle of the drive shaft (12) from the rotation angle at the peak discharge flow rate (90). Pump device.