Reciprocating Pump

Abstract

A reciprocating pump capable of suppressing the movement of lubricating oil when the reciprocating pump is inclined relative to the horizontal direction. [Solution] A reciprocating pump (1) according to the present invention comprises multiple pump units (PU), a motor (3), a rotating shaft (4), bearings (5), lubricating oil (Lb), multiple transmission mechanisms (TM), and a housing (2). The housing comprises multiple machine chambers (R2) and a partition (23). The partition has a communication hole (H1) and a valve (V) disposed in the communication hole. The communication hole is disposed below the lubricating oil level in the vertical direction. The valve closes when the tilt angle of the axial direction relative to the horizontal is equal to or greater than a valve closing angle, and opens when the tilt angle is less than the valve closing angle. The valve closing angle is the angle at which, after the valve closes, enough lubricating oil remains in each machine chamber to contact each of the multiple bearings with the lubricating oil when the rotating shaft is tilted to a predetermined tilt angle greater than the valve closing angle.

Description

[Technical Field]

[0001] The present invention relates to a reciprocating pump. [Background technology]

[0002] BACKGROUND ART A reciprocating pump including a pump unit, a motor, a rotating shaft, a transmission mechanism, a machine chamber, bearings, and lubricating oil is known (see, for example, Patent Document 1).

[0003] The pump unit sucks in and discharges the pumped liquid. The motor generates the power (rotational power) required for the operation (reciprocation) of the pump unit. The rotating shaft is connected to the motor and rotates in accordance with the rotation of the motor. The transmission mechanism transmits the power generated by the motor to the pump unit via the rotating shaft. The machine room houses the transmission mechanism. The bearings are arranged in the machine room and support the rotating shaft. Lubricating oil is stored inside the machine room and is used to lubricate the bearings.

[0004] Among such reciprocating pumps, there is a reciprocating pump (hereinafter referred to as a "conventional pump") that includes multiple pump units, multiple transmission mechanisms, and multiple machine chambers. In the conventional pump, the multiple machine chambers are arranged side by side along the axial direction of the rotating shaft and are connected to each other. Therefore, the common lubricating oil is distributed and stored approximately evenly in each of the multiple machine chambers. Therefore, when the axial direction of the rotating shaft of the conventional pump is inclined with respect to the horizontal direction, the lubricating oil may move between the multiple machine chambers and become unevenly concentrated in one of the machine chambers. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Japanese Patent Application Publication No. 9-170559 Summary of the Invention [Problem to be solved by the invention]

[0006] Here, conventional pumps are sometimes installed on vehicles (e.g., ships) that travel for long periods of time and used to supply fuel to the vehicle. In this case, the pumped liquid used in the conventional pump is, for example, liquefied petroleum gas (LPG). The liquefied petroleum gas is used as fuel for the vehicle. The vehicle oscillates around its respective axes (roll axis, pitch axis, and yaw axis) due to its surrounding environment (e.g., waves). Therefore, in a conventional pump installed on the vehicle, the axial direction of the rotating shaft tilts relative to the horizontal as the vehicle oscillates. At this time, due to the tilt in the axial direction of the rotating shaft, lubricating oil moves from a machine room located on one end of the rotating shaft (hereinafter referred to as the "one-end machine room") to a machine room located on the other end of the rotating shaft (hereinafter referred to as the "other-end machine room"). As a result, the lubricating oil is unevenly distributed in the other-end machine room, and the amount of lubricating oil stored inside the one-end machine room decreases. When the amount of oil decreases to a certain level (a level at which the bearing cannot come into contact with the lubricating oil), the bearing is no longer lubricated and the bearing's cooling effect is no longer achieved. In this case, direct contact between the metal components of the bearing (e.g., the rolling elements and the raceways) can damage the contact surfaces between these components. In addition, frictional resistance between these components increases, generating frictional heat. As a result, the bearing can seize and break.

[0007] This technical problem can be solved by a configuration in which the multiple machine chambers are separated by partitions so that they do not communicate with each other. In this case, the lubricating oil cannot move between the multiple machine chambers. In other words, even if the axial direction of the rotating shaft is tilted with respect to the horizontal, the amount of lubricating oil stored inside the machine chamber on one end does not decrease, and the bearing can come into contact with the lubricating oil.

[0008] One end of the connecting rod of the transmission mechanism is connected to the rotating shaft. When the rotating shaft rotates in response to the rotation of the motor, the one end of the connecting rod moves circularly within the machine chamber in response to the rotation of the rotating shaft. This causes a change in the volume of the space within the machine chamber. This volume change causes the internal pressure of the machine chamber to periodically increase and decrease. When the connecting rods of the multiple transmission mechanisms each move circularly, the rate of change in the volume of the space within the machine chamber in a configuration in which the multiple machine chambers are separated by partitions (i.e., the multiple machine chambers are not connected to each other) is greater than the rate of change in the volume of the space within the machine chamber in a configuration in which the multiple machine chambers are not separated by partitions (i.e., the multiple machine chambers are connected to each other). Furthermore, the phases of the movements of adjacent connecting rods in the axial direction are shifted by the same angle. Therefore, in a configuration in which the multiple machine chambers are not separated by partitions, the increases and decreases in the internal pressure and volume of each machine chamber are canceled out and suppressed. On the other hand, in a configuration in which multiple machine rooms are separated from each other by partition walls, the internal pressure and volume of each machine room periodically fluctuate greatly. At this time, components (e.g., sealing members) located in the machine rooms are subjected to loads based on the fluctuations in internal pressure. As a result, fatigue of the components is accelerated, shortening their lifespan. In this case, the replacement cycle for the components is also shortened. Therefore, a configuration in which multiple machine rooms are separated from each other by partition walls is not suitable for a reciprocating pump installed in a vehicle that travels for long periods of time.

[0009] An object of the present invention is to provide a reciprocating pump that can suppress the movement of lubricating oil when the reciprocating pump is inclined relative to the horizontal direction. [Means for solving the problem]

[0010] In one embodiment of the present invention, a reciprocating pump includes a plurality of pump units that suck and discharge pumped liquid, a motor that generates power required for the operation of each of the plurality of pump units, a rotating shaft connected to the motor, a plurality of bearings that support the rotating shaft, lubricating oil used to lubricate each of the plurality of bearings, a plurality of transmission mechanisms that transmit the power generated by the motor to corresponding pump units via the rotating shaft, and a housing that accommodates the rotating shaft and the plurality of transmission mechanisms, wherein the housing is provided with a plurality of machine chambers that accommodate corresponding transmission mechanisms and partition walls that separate the plurality of machine chambers, each of the plurality of machine chambers being arranged side by side along the axial direction of the rotating shaft, and the partition walls are arranged between adjacent machine chambers in the axial direction, and the partition walls separate adjacent front and rear machine chambers from each other. the valve is closed when the inclination angle of the axial direction with respect to the horizontal direction is equal to or greater than a valve closing angle, and opens when the inclination angle is less than the valve closing angle, and the valve closing angle is an angle at which the lubricating oil remains in each of the machine chambers in an amount that causes each of the bearings to come into contact with the lubricating oil when the axial direction is inclined to a predetermined inclination angle that is greater than the valve closing angle after the valve is closed. [Effects of the Invention]

[0011] The present invention can provide a reciprocating pump that can suppress the movement of lubricating oil when the reciprocating pump is inclined relative to the horizontal direction. [Brief explanation of the drawings]

[0012] [Figure 1] 1 is a schematic plan view of a reciprocating pump according to an embodiment of the present invention; [Figure 2] FIG. 2 is a schematic cross-sectional view of the reciprocating pump taken along line AA in FIG. [Figure 3] FIG. 2 is a schematic cross-sectional view of the reciprocating pump taken along line BB in FIG. 1. [Figure 4] 4 is a partially enlarged schematic cross-sectional view of the vicinity of the rotation shaft of the reciprocating pump taken along line CC in FIG. 3. [Figure 5] FIG. 2 is an enlarged schematic view of the vicinity of a valve of the reciprocating pump. [Figure 6] 3 is a schematic diagram of the reciprocating pump, showing the state of lubricating oil stored inside a machine chamber and a coupling chamber of the reciprocating pump. FIG. [Figure 7] 7 is a schematic diagram of the reciprocating pump, showing a state of lubricating oil stored inside a machine chamber and a coupling chamber of the reciprocating pump, different from that shown in FIG. 6. FIG. [Figure 8] 8 is a schematic diagram of the reciprocating pump, showing a state of lubricating oil stored inside a machine chamber and a coupling chamber of the reciprocating pump, different from that shown in FIG. 7. [Figure 9] FIG. 10 is an enlarged schematic view of a modified example of the reciprocating pump according to the present invention, showing the vicinity of a valve of the reciprocating pump. DETAILED DESCRIPTION OF THE INVENTION

[0013] An embodiment of a reciprocating pump (hereinafter referred to as "the pump") according to the present invention will be described below with reference to the drawings. In each drawing, the same members and elements are designated by the same reference numerals, and duplicate explanations will be omitted. Furthermore, the dimensional proportions of each element may be exaggerated for the sake of convenience, and are not limited to the proportions shown in each drawing.

[0014] ●Configuration of this pump First, the configuration of this pump will be described below. In the following description, unless otherwise specified, the axial direction of the rotating shaft is assumed to be parallel to the horizontal direction.

[0015] FIG. 1 is a schematic plan view of the pump, showing an embodiment of the pump. FIG. 2 is a schematic cross-sectional view of the pump 1 taken along line AA in FIG. FIG. 3 is a schematic cross-sectional view of the pump 1 taken along line BB in FIG. In FIG. 3, the dashed line indicates the position of the liquid surface of the lubricating oil, which will be described later.

[0016] The pump 1 is a diaphragm pump that sucks in and discharges a handled liquid W. The pump 1 is installed, for example, on a vehicle (e.g., a ship) that travels for long periods of time and is used to supply fuel to the vehicle. The "handled liquid W" is, for example, liquefied petroleum gas (LPG). The liquefied petroleum gas is used as fuel for the vehicle. The pump 1 includes a housing 2, a motor 3, a rotating shaft 4, a plurality (six) of bearings 5a, 5b, 5c, 5d, 5e, and 5f, a plurality (two) of couplings 6a and 6b, lubricating oil Lb, a plurality (three) of connecting rods 7, a plurality (three) of coupling members 8, a plurality (three) of plungers 9, and a plurality (three) of diaphragms 10.

[0017] In the following description, when the bearings 5a to 5f are not particularly distinguished from one another, the bearings 5a to 5f are collectively referred to as bearings 5. When the couplings 6a and 6b are not particularly distinguished from one another, the couplings 6a and 6b are collectively referred to as couplings 6.

[0018] In the following description, the "front-rear direction" refers to the reciprocating direction of the plunger 9. The "front direction" refers to the direction in which the plunger 9 moves in order for the pump 1 to discharge the pumped fluid W. The "rear direction" refers to the direction in which the plunger 9 moves in order for the pump 1 to suck in the pumped fluid W. The "downward direction" refers to the direction of gravity, and the "upward direction" refers to the opposite direction of the downward direction. The "leftward direction" refers to the direction in which the motor 3 is disposed relative to the rotating shaft 4 (the direction in which one end of the rotating shaft 4 is oriented in the axial direction), and the "rightward direction" refers to the opposite direction of the leftward direction (the direction in which the other end of the rotating shaft 4 is oriented in the axial direction). The leftward direction is an example of the first direction in the present invention. The rightward direction is an example of the second direction in the present invention. In the following description, the axial direction of the rotating shaft 4 is assumed to be parallel to the left-right direction.

[0019] In the present invention, the handled liquid W is not limited to liquefied petroleum gas, and may be, for example, liquefied natural gas or liquefied ammonia.

[0020] The housing 2 houses the rotating shaft 4, bearings 5, coupling 6, connecting rod 7, connecting member 8, plunger 9, and diaphragm 10. The housing 2 is made of metal. The housing 2 includes a plurality of (three) pump chambers R1, a plurality of (three) suction pipes 21, a plurality of (three) discharge pipes 22, a plurality of (three) machine chambers R2a, R2b, R2c, a plurality of (two) partition walls 23, and a plurality of (five) lubricating oil reservoirs 24.

[0021] In the following description, when the machine rooms R2a to R2c are not particularly distinguished from one another, the machine rooms R2a to R2c are collectively referred to as the machine room R2.

[0022] Each of the plurality of pump chambers R1 houses a corresponding diaphragm 10. In the pump chamber R1, the diaphragm 10 reciprocates, causing the pumped liquid W to be sucked in from the suction pipe 21 and discharged to the discharge pipe 22. The front end of the housing 2 constitutes the pump chamber R1. That is, the pump chamber R1 is disposed at the front end of the housing 2.

[0023] The suction pipe 21 is a flow path through which the pumped liquid W flows to be sucked into the corresponding pump chamber R1. The suction pipe 21 is connected to the lower end of the pump chamber R1.

[0024] The discharge pipe 22 is a flow path through which the treated fluid W discharged from the pump chamber R1 flows. The discharge pipe 22 is connected to the upper end of the pump chamber R1.

[0025] Each of the multiple machine chambers R2 accommodates a rotating shaft 4, a corresponding bearing 5, a corresponding connecting rod 7, a corresponding coupling member 8, and a corresponding plunger 9. A portion of the housing 2 rearward of the pump chamber R1 (the front end portion of the housing 2) constitutes a machine chamber R2 corresponding to the pump chamber R1. The multiple machine chambers R2 are arranged side by side along the axial direction. The machine chamber R2a is arranged on the leftmost side of the machine chambers R2a to R2c. The machine chamber R2c is arranged on the rightmost side of the machine chambers R2a to R2c. The machine chamber R2b is arranged between the machine chambers R2a and R2c. That is, the machine chamber R2b is arranged to the right of the machine chamber R2a and adjacent to the machine chamber R2a. The machine chamber R2c is arranged to the right of the machine chamber R2b and adjacent to the machine chamber R2b. The machine chamber R2a is an example of a first machine chamber in the present invention. The machine room R2b is an example of the second machine room defined in the present invention.

[0026] FIG. 4 is a partially enlarged schematic cross-sectional view of the vicinity of the rotation shaft 4 taken along line CC in FIG. For ease of explanation, the drawing shows a simplified view of the vicinity of the rotation axis 4. In the following description, FIGS. 1 to 3 will be referred to along with FIG. 4 as appropriate.

[0027] The partition wall 23 divides the multiple machine chambers R2. The partition wall 23 includes a partition wall 23a and a partition wall 23b. The partition wall 23a divides the machine chamber R2a from the machine chamber R2b. The partition wall 23b divides the machine chamber R2b from the machine chamber R2c. In the axial direction, the partition wall 23a is disposed between the machine chamber R2a and the machine chamber R2b. In the axial direction, the partition wall 23b is disposed between the machine chamber R2b and the machine chamber R2c. In other words, in the axial direction, the partition wall 23 is disposed between adjacent machine chambers R2. The partition wall 23 includes multiple (2) coupling chambers R3a, R3b, multiple (24) liquid communication holes H1, multiple (24) gas communication holes H2, and multiple (24) valves V.

[0028] In the following description, when the coupling chambers R3a and R3b are not particularly distinguished from each other, the coupling chambers R3a and R3b will be collectively referred to as the coupling chamber R3.

[0029] The coupling chamber R3a accommodates the coupling 6a. The coupling chamber R3b accommodates the coupling 6b. In other words, the coupling chamber R3 accommodates the corresponding coupling 6. The coupling chamber R3a is disposed inside the partition wall 23a. That is, the coupling chamber R3a is disposed between the machine chamber R2a and the machine chamber R2b. The coupling chamber R3b is disposed inside the partition wall 23b. That is, the coupling chamber R3b is disposed between the machine chamber R2b and the machine chamber R2c. In other words, the coupling chamber R3 is disposed between the adjacent machine chambers R2.

[0030] The liquid communication holes H1 are through-holes that connect adjacent machine chambers R2 among the machine chambers R2a to R2c. In the axial direction, the liquid communication holes H1 penetrate the corresponding partition walls 23 in the left-right direction. In other words, the penetration direction of the liquid communication holes H1 is parallel to the axial direction. In the up-down direction, each of the multiple liquid communication holes H1 is positioned below the liquid level of the lubricating oil Lb. In other words, each of the multiple liquid communication holes H1 is immersed in the lubricating oil Lb. The multiple liquid communication holes H1 include a plurality (6) of first liquid communication holes H1a, a plurality (6) of second liquid communication holes H1b, a plurality (6) of third liquid communication holes H1c, and a plurality (6) of fourth liquid communication holes H1d. The liquid communication holes H1 are an example of a communication hole defined in the present invention.

[0031] In the present invention, the penetrating direction of the liquid communication hole H1 need only be parallel to an imaginary plane that is parallel to the front-rear direction and the left-right direction, and does not have to be parallel to the axial direction.

[0032] Furthermore, in the present invention, among the multiple liquid communication holes H1, some of the liquid communication holes H1 do not have to be immersed in the lubricating oil Lb.

[0033] The first liquid communication hole H1a communicates between the coupling chamber R3a and the machine chamber R2a. The second liquid communication hole H1b communicates between the coupling chamber R3a and the machine chamber R2b. That is, the first liquid communication hole H1a and the second liquid communication hole H1b communicate between the machine chamber R2a and the machine chamber R2b via the coupling chamber R3a. The third liquid communication hole H1c communicates between the coupling chamber R3b and the machine chamber R2b. The fourth liquid communication hole H1d communicates between the coupling chamber R3b and the machine chamber R2c. That is, the third liquid communication hole H1c and the fourth liquid communication hole H1d communicate between the machine chamber R2b and the machine chamber R2c via the coupling chamber R3b. In the axial direction, the first liquid communication hole H1a is disposed between the coupling chamber R3a and the machine chamber R2a. In the axial direction, the second liquid communication hole H1b is disposed between the coupling chamber R3a and the machine chamber R2b. In the axial direction, the third liquid communication hole H1c is disposed between the coupling chamber R3b and the machine chamber R2b. In the axial direction, the fourth liquid communication hole H1d is disposed between the coupling chamber R3b and the machine chamber R2c. The first liquid communication hole H1a and the third liquid communication hole H1c are examples of first communication holes in the present invention. The second liquid communication hole H1b and the fourth liquid communication hole H1d are examples of second communication holes in the present invention.

[0034] The gas communication holes H2 are through-holes that connect adjacent machine chambers R2 among the machine chambers R2a to R2c. In the axial direction, the gas communication holes H2 penetrate the corresponding partition walls 23 in the left-right direction. In the vertical direction, each of the multiple gas communication holes H2 is positioned above the liquid surface of the lubricating oil Lb. In other words, each of the multiple gas communication holes H2 is not immersed in the lubricating oil Lb. The multiple gas communication holes H2 include a plurality (6) of first gas communication holes H2a, a plurality (6) of second gas communication holes H2b, a plurality (6) of third gas communication holes H2c, and a plurality (6) of fourth gas communication holes H2d.

[0035] The first gas communication hole H2a communicates between the coupling chamber R3a and the machine chamber R2a. The second gas communication hole H2b communicates between the coupling chamber R3a and the machine chamber R2b. That is, the first gas communication hole H2a and the second gas communication hole H2b communicate between the machine chamber R2a and the machine chamber R2b via the coupling chamber R3a. The third gas communication hole H2c communicates between the coupling chamber R3b and the machine chamber R2b. The fourth gas communication hole H2d communicates between the coupling chamber R3b and the machine chamber R2c. That is, the third gas communication hole H2c and the fourth gas communication hole H2d communicate between the machine chamber R2b and the machine chamber R2c via the coupling chamber R3b. In the axial direction, the first gas communication hole H2a is arranged between the coupling chamber R3a and the machine chamber R2a. In the axial direction, the second gas communication hole H2b is arranged between the coupling chamber R3a and the machine chamber R2b. In the axial direction, the third gas communication hole H2c is arranged between the coupling chamber R3b and the machine chamber R2b. In the axial direction, the fourth gas communication hole H2d is arranged between the coupling chamber R3b and the machine chamber R2c.

[0036] The valve V opens and closes based on the tilt angle of the axial direction of the rotation shaft 4 relative to the horizontal direction (hereinafter simply referred to as the "tilt angle"). The valve V closes when the tilt angle is equal to or greater than the closing valve angle described below. The valve V opens when the tilt angle is less than the closing valve angle. Each of the multiple valves V is disposed in a corresponding liquid communication hole H1. The valve V has multiple (24) valve bodies V1 and multiple (48) valve seat surfaces V2. That is, each of the multiple valves V has one valve body V1 and two valve seat surfaces V2. The opening and closing of the valve V will be described in detail below.

[0037] The valve element V1 is housed in the corresponding liquid communication hole H1 and moves within the liquid communication hole H1 in the axial direction (the penetrating direction of the liquid communication hole H1) according to the tilt angle. That is, a portion of the liquid communication hole H1 functions as a valve chamber for the corresponding valve element V1. In other words, the valve element V1 is housed in the corresponding valve chamber (a portion of the corresponding liquid communication hole H1). The valve element V1 is made of a material (e.g., stainless steel) that has a specific gravity greater than that of the lubricating oil Lb. The shape of the valve element V1 is designed to correspond to the shape of the valve seat surface V2 for the valve element V1, and in this embodiment is spherical.

[0038] The valve seat surface V2 is the surface against which the valve disc V1 abuts when the valve V is closed. The two valve seat surfaces V2 are arranged in the liquid communication hole H1 so as to sandwich the valve disc V1 in the axial direction. A portion of the liquid communication hole H1 functions as the valve seat surface V2. That is, the inner diameter of a portion of the liquid communication hole H1 continuously increases in the direction in which the valve disc V1 is arranged, thereby forming the valve seat surface V2. That is, the valve seat surface V2 is an inclined surface. When the axial direction of the rotation shaft 4 is inclined to the valve closing angle with respect to the horizontal direction, the valve disc V1 abuts against the corresponding valve seat surface V2 and blocks the corresponding liquid communication hole H1.

[0039] The lubricant oil reservoir 24 stores lubricant oil Lb. The lower half of each of the multiple machine chambers R2 and the lower half of each of the multiple coupling chambers R3 function as the lubricant oil reservoir 24. That is, the lubricant oil reservoir 24 is disposed in the lower half of each of the multiple machine chambers R2 and the lower half of each of the multiple coupling chambers R3.

[0040] The motor 3 generates the power (rotational power) required for the operation (reciprocation) of the diaphragm 10.

[0041] The rotating shaft 4 is connected to the motor 3 and rotates in response to the rotation of the motor 3. The rotating shaft 4 is made of metal. The rotating shaft 4 is, for example, cylindrical. The rotating shaft 4 is arranged so that the axial direction of the rotating shaft 4 is parallel to the left-right direction, i.e., so that the axial direction of the rotating shaft 4 is perpendicular to the front-rear direction and the up-down direction. The rotating shaft 4 includes a first individual rotating shaft 4a, a second individual rotating shaft 4b, and a third individual rotating shaft 4c.

[0042] The first individual rotating shaft 4a is connected to the motor 3 and rotates in response to the rotation of the motor 3. The second individual rotating shaft 4b is connected to the first individual rotating shaft 4a via a coupling 6a and rotates in response to the rotation of the first individual rotating shaft 4a. The third individual rotating shaft 4c is connected to the second individual rotating shaft 4b via a coupling 6b and rotates in response to the rotation of the second individual rotating shaft 4b. The first individual rotating shaft 4a to the third individual rotating shaft 4c are arranged side by side along the axial direction. The first individual rotating shaft 4a is arranged on the leftmost side of the first individual rotating shaft 4a to the third individual rotating shaft 4c. The third individual rotating shaft 4c is arranged on the rightmost side of the first individual rotating shaft 4a to the third individual rotating shaft 4c. The second individual rotating shaft 4b is arranged between the first individual rotating shaft 4a and the third individual rotating shaft 4c. That is, the second individual rotating shaft 4b is disposed to the right of the first individual rotating shaft 4a and adjacent to the first individual rotating shaft 4a. The third individual rotating shaft 4c is disposed to the right of the second individual rotating shaft 4b and adjacent to the second individual rotating shaft 4b. Each of the first individual rotating shaft 4a to the third individual rotating shaft 4c is an example of an individual rotating shaft according to the present invention.

[0043] The bearings 5 ​​are, for example, rolling bearings. Bearings 5a and 5b support the first individual rotating shaft 4a. Bearings 5c and 5d support the second individual rotating shaft 4b. Bearings 5e and 5f support the third individual rotating shaft 4c. In other words, the bearings 5 ​​support the rotating shaft 4. When the axial direction of the rotating shaft 4 is parallel to the horizontal direction, the lower half of each of the multiple bearings 5 ​​is immersed in the lubricating oil Lb. In other words, when the axial direction of the rotating shaft 4 is parallel to the horizontal direction, each of the multiple bearings 5 ​​is in contact with the lubricating oil Lb. In the axial direction, bearing 5a is arranged at the left end of the machine chamber R2a. In the axial direction, bearing 5b is arranged at the right end of the machine chamber R2a. In the axial direction, bearing 5c ​​is arranged at the left end of the machine chamber R2b. In the axial direction, bearing 5d is arranged at the right end of the machine chamber R2b. In the axial direction, bearing 5e is arranged at the left end of the machine chamber R2c. In other words, the bearings 5 ​​are respectively arranged at both ends of the corresponding machine chamber R2 in the axial direction.

[0044] The coupling 6 is, for example, a known gear coupling. The coupling 6a is housed in the coupling chamber R3a, and the coupling 6b is housed in the coupling chamber R3b. In the axial direction, the coupling 6a is disposed between the first individual rotating shaft 4a and the second individual rotating shaft 4b, and connects the first individual rotating shaft 4a and the second individual rotating shaft 4b to each other. In the axial direction, the coupling 6b is disposed between the second individual rotating shaft 4b and the third individual rotating shaft 4c, and connects the second individual rotating shaft 4b and the third individual rotating shaft 4c to each other. In other words, in the axial direction, the coupling 6 connects adjacent individual rotating shafts (the first individual rotating shaft 4a to the third individual rotating shaft 4c) to each other. As a result, each of the first individual rotating shaft 4a to the third individual rotating shaft 4c constitutes a rotating shaft 4. When the axial direction of the rotating shaft 4 is parallel to the horizontal direction, the lower half of each of the multiple couplings 6 is immersed in lubricating oil Lb. That is, when the axial direction of the rotary shaft 4 is parallel to the horizontal direction, each of the plurality of couplings 6 is in contact with the lubricating oil Lb.

[0045] The lubricating oil Lb is oil used to lubricate each of the plurality of bearings 5 ​​and each of the plurality of couplings 6. The lubricating oil Lb is stored inside each of the plurality of machine chambers R2 and each of the plurality of coupling chambers R3 (lubricating oil reservoir 24).

[0046] The connecting rod 7 transmits the power of the motor 3, which is transmitted via the rotating shaft 4, to the connecting member 8. The connecting rod 7 is made of metal. The connecting rod 7 is connected to the rotating shaft 4 and the rear end of the connecting member 8.

[0047] The connecting member 8 transmits the power (reciprocating power) transmitted from the connecting rod 7 to the plunger 9. The connecting member 8 is made of metal. The connecting member 8 reciprocates in the front-rear direction due to the power (reciprocating power) transmitted by the connecting rod 7. The front end of the connecting member 8 is connected to the rear end of the plunger 9.

[0048] The plunger 9 reciprocates back and forth based on the power transmitted from the connecting member 8, thereby reciprocating the diaphragm 10. The plunger 9 is made of metal. The front end of the plunger 9 is connected to the rear surface of the diaphragm 10.

[0049] The diaphragm 10 reciprocates to draw the pumped fluid W into the pump chamber R1 and discharge the pumped fluid W from the pump chamber R1. The diaphragm 10 is housed in the pump chamber R1. The outer edge of the diaphragm 10 is fixed to the housing 2 with both surfaces of the diaphragm 10 facing in the front-to-rear direction.

[0050] As described above, the plunger 9 is connected to the connecting member 8. Therefore, when the rotating shaft 4 is rotated by the power of the motor 3, causing the connecting member 8 to reciprocate in the front-to-rear direction, the plunger 9 reciprocates in the front-to-rear direction together with the connecting member 8 in conjunction with the reciprocating movement of the connecting member 8. When the plunger 9 reciprocates in the front-to-rear direction, the diaphragm 10 also reciprocates in the front-to-rear direction, thereby increasing or decreasing the volume (pressure) within the pump chamber R1. As a result, the pumped liquid W is sucked from the suction pipe 21 into the pump chamber R1, and the sucked pumped liquid W is discharged from the pump chamber R1 to the discharge pipe 22.

[0051] In this manner, the connecting rod 7 and the coupling member 8 constitute a transmission mechanism TM that transmits power generated by the motor 3 to the plunger 9 via the rotating shaft 4. The pump chamber R1, plunger 9, and diaphragm 10 constitute a pump unit PU that sucks in and discharges the pumped fluid W. In other words, the transmission mechanism TM transmits the power generated by the motor 3, required for the operation of each of the multiple pump units PU, to the corresponding pump unit PU via the rotating shaft 4. That is, the pump 1 comprises multiple (three) transmission mechanisms TM and multiple (three) pump units PU. The transmission mechanism TM comprises a connecting rod 7 and the coupling member 8. The pump unit PU comprises a pump chamber R1, a plunger 9, and a diaphragm 10. The housing 2 accommodates each of the multiple transmission mechanisms TM and each of the multiple pump units PU. Each of the multiple machine chambers R2 accommodates a corresponding transmission mechanism TM. The first to third individual rotating shafts 4a to 4c correspond to each of the multiple pump units PU.

[0052] ●Lubrication of bearings and couplings● Next, the lubrication of the bearing 5 and the coupling 6 will be explained below. In the following explanation, FIGS. 1 to 4 will be referred to as appropriate.

[0053] In the following description, the "parallel state" refers to a state in which the axial direction of the rotating shaft 4 is parallel to the horizontal direction (the axial direction of the rotating shaft 4 is not tilted relative to the horizontal direction). In other words, the balanced state refers to a state in which the tilt angle is 0°. The "tilted state" refers to a state in which the axial direction of the rotating shaft 4 is not parallel to the horizontal direction (the axial direction of the rotating shaft 4 is tilted relative to the horizontal direction). In other words, the tilted state refers to a state in which the tilt angle is not 0°.

[0054] ●Lubrication of bearings and couplings in parallel First, the lubrication of the bearing 5 and the coupling 6 in the parallel state will be explained below.

[0055] FIG. 5 is an enlarged schematic view of the vicinity of the valve V in FIG. 5, (a) shows the state of the valve V in the parallel state. Details of (b) and (c) will be described later.

[0056] As mentioned above, the penetration direction of the liquid communication hole H1 is parallel to the axial direction. The valve element V1 moves along the axial direction within the liquid communication hole H1 according to the tilt angle. Therefore, in the parallel state, the valve element V1 does not move within the liquid communication hole H1. In other words, the valve element V1 does not block the liquid communication hole H1. In other words, the valve V is open.

[0057] In the parallel state, the lubricating oil Lb can move between the interiors of the multiple machine chambers R2 and the multiple coupling chambers R3 (the lubricating oil reservoir 24) through the multiple liquid communication holes H1. Therefore, the lubricating oil Lb moves slightly between the interiors of the multiple machine chambers R2 and the multiple coupling chambers R3 (the lubricating oil reservoir 24) due to the operation of the pump 1. At this time, the lubricating oil Lb stored in the interiors of the multiple machine chambers R2 and the multiple coupling chambers R3 (the lubricating oil reservoir 24) is not separated by the valve V and the partition wall 23. The liquid levels of the lubricating oil Lb in the interiors of the multiple machine chambers R2 and the multiple coupling chambers R3 (the lubricating oil reservoir 24) are approximately the same (to a height such that the lower half of each of the multiple bearings 5 ​​and the lower half of each of the multiple couplings 6 are immersed in the lubricating oil Lb). In other words, in the parallel state, each of the multiple bearings 5 ​​and each of the multiple couplings 6 are in contact with the lubricating oil Lb. Therefore, even if the rotating shaft 4 rotates in response to the rotation of the motor 3, the bearing 5 and the coupling 6 are lubricated by the lubricating oil Lb and are therefore unlikely to be damaged.

[0058] Here, the connecting rod 7 transmits the power of the motor 3 transmitted via the rotary shaft 4 to the coupling member 8. At this time, the rear end of the connecting rod 7 moves circularly, and the front end of the connecting rod 7 moves back and forth in the front-to-rear direction. The phases of the movements of adjacent connecting rods 7 in the axial direction are shifted by the same angle (120°). In addition, the coupling member 8 moves back and forth in the front-to-rear direction due to the power (reciprocating power) transmitted by the connecting rod 7.

[0059] Generally, when a connecting rod makes circular motion within a machine chamber, the volume of the space within the machine chamber changes. This volume change periodically increases and decreases the internal pressure of the machine chamber. However, as described above, in the present pump 1, each of the multiple machine chambers R2 and each of the multiple coupling chambers R3 are interconnected via the corresponding liquid communication holes H1. In the vertical direction, each of the multiple liquid communication holes H1 is positioned below the liquid level of the lubricating oil Lb. Therefore, the liquid-phase lubricating oil Lb in the machine chamber R2 can move through each of the multiple machine chambers R2 and each of the multiple coupling chambers R3 via the multiple liquid communication holes H1. In the present pump 1, each of the multiple machine chambers R2 and each of the multiple coupling chambers R3 are also interconnected via the corresponding gas communication holes H2. In the vertical direction, each of the multiple gas communication holes H2 is positioned above the liquid level of the lubricating oil Lb. Therefore, gas (e.g., air) in the gas phase within the machine chamber R2 can move through each of the multiple machine chambers R2 and each of the multiple coupling chambers R3 via each of the multiple gas communication holes H2. In other words, the volume of the space within the machine chamber R2 is larger than the volume of the space within the machine chamber in a configuration in which the machine chambers and the coupling chambers are not connected to each other. In other words, when the connecting member 8 reciprocates in the front-to-rear direction, the volumetric change rate of the space within the machine chamber R2 is smaller than the volumetric change rate in the same configuration. Furthermore, due to the phase shift described above, increases and decreases in the internal pressure and volume of each machine chamber R2 cancel each other out. Therefore, increases and decreases in the internal pressure of the machine chamber R2 are suppressed.

[0060] Lubrication of bearings and couplings when tilted Next, the lubrication of the bearing 5 and the coupling 6 in the tilted state will be explained below.

[0061] As described above, the pump 1 is installed (placed) on the floor of a ship (not shown; the same applies below) that sails for long periods of time. The ship sways around its various axes (roll axis, pitch axis, and yaw axis) due to its surrounding environment (e.g., waves). Therefore, the axial direction of the rotating shaft 4 of the pump 1 tilts relative to the horizontal as the ship sways.

[0062] Here, Nippon Kaiji Kyokai, which sets regulations regarding pumps (hereinafter referred to as "auxiliary machinery") installed on ships, specifies that "the auxiliary machinery must be designed so that it can operate under specified conditions when installed on the ship." This condition includes a condition regarding the inclination angle. The inclination angle condition specifies that the inclination angle of the auxiliary machinery around the roll axis must be "22.5°." In other words, the maximum inclination angle (hereinafter referred to as "maximum inclination angle") is "22.5°." The maximum inclination angle is an example of the specified inclination angle in the present invention.

[0063] In the following description, it is assumed that the axial direction of the rotating shaft 4 is tilted counterclockwise with respect to the horizontal when viewed from the rear. The description of the lubrication of the bearings 5 ​​and the coupling 6 when the axial direction of the rotating shaft 4 is tilted clockwise with respect to the horizontal when viewed from the rear is omitted because it is the same as the description below except that the left-right direction is reversed. When the axial direction of the rotating shaft 4 is tilted counterclockwise with respect to the horizontal when viewed from the rear, the positions of the multiple bearings 5 ​​increase from left to right. That is, when the axial direction of the rotating shaft 4 is tilted counterclockwise with respect to the horizontal when viewed from the rear, the position of bearing 5f, which is located on the rightmost side of the multiple bearings 5, is higher than the positions of bearings 5a to 5e, and the position of bearing 5a, which is located on the leftmost side of the multiple bearings 5, is lower than the positions of bearings 5b to 5f. Here, in the axial direction, coupling 6a is disposed between bearing 5b and bearing 5c, and coupling 6b is disposed between bearing 5d and bearing 5e. Therefore, in order for all bearings 5 ​​and couplings 6 to come into contact with lubricating oil Lb, the amount of lubricating oil Lb stored in the machine chamber R2c in which bearing 5f is located must be an amount that allows bearing 5f to come into contact with lubricating oil Lb.

[0064] In FIG. 5, (b) shows the state of the valve V when the axial direction of the rotary shaft 4 is tilted counterclockwise at an angle θ1° with respect to the horizontal direction as viewed from behind.

[0065] First, when viewed from the rear, when the axial direction of the rotating shaft 4 is tilted counterclockwise by "an angle θ1° (for example, approximately 1° to 2°)" with respect to the horizontal, the valve element V1 moves leftward within the liquid communication hole H1. At this time, the valve element V1 abuts against the valve seat surface V2 and does not block the liquid communication hole H1. In other words, the valve V is open. When the valve V is open, the lubricating oil Lb moves leftward within the liquid communication hole H1 so as to equalize the liquid levels of the lubricating oil Lb in all of the lubricating oil reservoirs 24.

[0066] Figure 6 is a schematic diagram of the pump 1, viewed from the rear, showing the state of the lubricating oil Lb stored inside the machine chamber R2 and the coupling chamber R3 when the axial direction of the rotating shaft 4 is tilted counterclockwise at an angle of θ1° relative to the horizontal. In FIG. 6, the broken line indicates the liquid level of the lubricating oil Lb. For ease of explanation, the pump 1 is shown in a simplified form in the drawing.

[0067] As described above, the common lubricant Lb is stored inside each of the multiple machine chambers R2 and each of the multiple coupling chambers R3 (lubricant reservoirs 24). The liquid communication holes H1 connect adjacent machine chambers R2 to each other via the coupling chambers R3. Therefore, the lubricant Lb stored inside the machine chambers R2b, R2c and the coupling chambers R3a, R3b moves leftward through the corresponding liquid communication holes H1 so as to equalize the liquid levels of the lubricant Lb in all of the lubricant reservoirs 24. That is, the lubricant Lb stored in the machine chamber R2c moves to the coupling chamber R3b. The lubricant Lb stored in the coupling chamber R3b moves to the machine chamber R2b. The lubricant Lb stored in the machine chamber R2b moves to the coupling chamber R3a. The lubricant Lb stored in the coupling chamber R3a moves to the machine chamber R2a. As a result, the amount of lubricating oil Lb stored inside the leftmost machine chamber R2a among the multiple machine chambers R2 increases slightly, and the amount of lubricating oil Lb stored inside the rightmost machine chamber R2c decreases slightly. That is, the lubricating oil Lb is slightly unevenly distributed in the machine chamber R2a. At this time, the amount of lubricating oil Lb stored inside the machine chamber R2a is greater than the amount of lubricating oil Lb stored inside the machine chamber R2b. The amount of lubricating oil Lb stored inside the machine chamber R2b is greater than the amount of lubricating oil Lb stored inside the machine chamber R2c. The amount of lubricating oil Lb stored inside the coupling chamber R3a is greater than the amount of lubricating oil Lb stored inside the coupling chamber R3b. At this time, the amount of lubricating oil Lb stored inside the machine chamber R2c is sufficient to bring the bearing 5f into contact with the lubricating oil Lb (see FIG. 6).

[0068] Return to Figure 5. In FIG. 5, (c) shows the state of the valve V when the axial direction of the rotary shaft 4 is tilted counterclockwise at an angle θ2° with respect to the horizontal direction as viewed from behind.

[0069] Next, when viewed from the rear, when the axial direction of the rotating shaft 4 is tilted counterclockwise by an angle θ2° (for example, approximately 2° to 5°, hereinafter referred to as the "valve closing angle") with respect to the horizontal, the valve disc V1 further moves leftward within the liquid communication hole H1 (angle θ1°<angle θ2°). At this time, the valve disc V1 abuts against the valve seat surface V2 and blocks the liquid communication hole H1. In other words, the valve V is closed. In this way, the valve V is closed when the tilt angle is equal to or greater than the valve closing angle. On the other hand, the valve V is open when the tilt angle is less than the valve closing angle. Here, the valve closing angle is set to be less than the maximum tilt angle. In other words, the maximum tilt angle is greater than the valve closing angle. When the valve V is closed, the lubricating oil Lb does not move leftward within the liquid communication hole H1. In other words, when viewed from the rear, even if the axial direction of the rotating shaft 4 is further tilted counterclockwise (more than the closing valve angle) relative to the horizontal direction, the amount of lubricating oil Lb stored (remaining) inside each of the multiple machine chambers R2 and each of the multiple coupling chambers R3 (lubricating oil reservoir 24) does not change.

[0070] Figure 7 is a schematic diagram of the pump 1, viewed from the rear, showing the state of the lubricating oil Lb stored inside the machine chamber R2 and the coupling chamber R3 immediately after the valve V closes, with the axial direction of the rotating shaft 4 tilted counterclockwise at an angle of θ2° relative to the horizontal. In FIG. 7, the broken line indicates the liquid level of the lubricating oil Lb. For ease of explanation, the pump 1 is shown in a simplified form in the drawing.

[0071] When viewed from the rear, when the axial direction of the rotating shaft 4 is tilted counterclockwise by the "valve closing angle" with respect to the horizontal, the amount of lubricating oil Lb stored inside the machine chamber R2c is maintained at an amount that allows the bearing 5f to be sufficiently exposed to the lubricating oil Lb. Similarly, the amount of lubricating oil Lb stored inside the coupling chamber R3b is maintained at an amount that allows the coupling 6b to be sufficiently exposed to the lubricating oil Lb.

[0072] Next, in a rear view, the axial direction of the rotation shaft 4 is tilted counterclockwise with respect to the horizontal direction up to the "maximum tilt angle (22.5°)".

[0073] Figure 8 is a schematic diagram of the pump 1, showing the state of the lubricating oil Lb stored inside the machine chamber R2 and the coupling chamber R3 when the axial direction of the rotating shaft 4 is tilted counterclockwise at the "maximum tilt angle" relative to the horizontal direction, as viewed from the rear. In FIG. 8, the broken line indicates the liquid level of the lubricating oil Lb. For ease of explanation, the pump 1 is shown in a simplified form in the drawing.

[0074] As described above, the valve V is closed when the tilt angle is equal to or greater than the valve closing angle. Therefore, the valve V remains closed while the tilt angle changes from the valve closing angle to the maximum tilt angle. At this time, the amount of lubricating oil Lb stored (remaining) inside each of the multiple machine chambers R2 and each of the multiple coupling chambers R3 (lubricating oil reservoir 24) does not change.

[0075] When viewed from the rear, when the tilt angle is changed to the maximum counterclockwise angle, the amount of lubricating oil Lb stored inside the machine chamber R2c is maintained at an amount that allows the bearing 5f to come into contact with the lubricating oil Lb. Also, the amount of lubricating oil Lb stored inside the coupling chamber R3b is maintained at an amount that allows the coupling 6b to come into contact with the lubricating oil Lb. Therefore, the amount of lubricating oil Lb stored (remaining) inside each of the multiple machine chambers R2 and each of the multiple coupling chambers R3 is maintained at an amount that allows each of the multiple bearings 5 ​​and each of the multiple couplings 6 to come into contact with the lubricating oil Lb. In this way, after the valve V closes, when the axial direction of the rotating shaft 4 tilts to the horizontal direction to the maximum tilt angle that is greater than the valve closing angle (when the tilt angle changes to the maximum tilt angle), the valve V closes at an angle (valve closing angle) such that an amount of lubricating oil Lb is stored (remains) inside each of the multiple machine chambers R2 and the multiple coupling chambers R3 so that each of the multiple bearings 5 ​​and each of the multiple couplings 6 comes into contact with the lubricating oil Lb. Therefore, even if the axial direction of the rotating shaft 4 tilts to the maximum tilt angle counterclockwise with respect to the horizontal direction as viewed from the rear, the bearings 5 ​​and the couplings 6 are lubricated by the lubricating oil Lb and are unlikely to be damaged.

[0076] Summary As described above, the pump 1 includes multiple pump units PU, a motor 3, a rotating shaft 4, multiple bearings 5, lubricating oil Lb, multiple transmission mechanisms TM, and a housing 2. Each of the multiple pump units PU sucks in and discharges the pumped liquid W. The motor 3 generates the power required to operate each of the multiple pump units PU. The rotating shaft 4 is connected to the motor 3. Each of the multiple bearings 5 ​​supports the rotating shaft 4. The lubricating oil Lb is used to lubricate each of the multiple bearings 5. Each of the multiple transmission mechanisms TM transmits the power generated by the motor 3 to the corresponding pump unit PU via the rotating shaft 4. The housing 2 houses the rotating shaft 4 and each of the multiple transmission mechanisms TM. The housing 2 includes multiple machine chambers R2 and a partition wall 23. Each of the multiple machine chambers R2 houses a corresponding transmission mechanism TM. The multiple machine chambers R2 are arranged side by side along the axial direction of the rotating shaft 4. The partition wall 23 separates each of the multiple machine chambers R2. In the axial direction, the partition wall 23 is disposed between adjacent machine chambers R2. The partition wall 23 is provided with a liquid communication hole H1 and a valve V. The liquid communication hole H1 connects adjacent machine chambers R2 among the multiple machine chambers R2. The valve V is disposed in the liquid communication hole H1. In the axial direction, each of the multiple bearings 5 ​​is disposed at both ends of the corresponding machine chamber R2. Lubricating oil Lb is stored inside each of the multiple machine chambers R2. In the vertical direction, the liquid communication hole H1 is disposed below the liquid level of the lubricating oil Lb. When the axial direction of the rotating shaft 4 is parallel to the horizontal direction, each of the multiple bearings 5 ​​is in contact with the lubricating oil Lb. The valve V closes when the tilt angle is equal to or greater than the valve closing angle, and opens when the tilt angle is less than the valve closing angle. The closing valve angle is the angle at which, after the valve V closes, the axial direction of the rotating shaft 4 is tilted to the maximum tilt angle greater than the closing valve angle (when the tilt angle changes to the maximum tilt angle), and an amount of lubricating oil Lb that allows each of the multiple bearings 5 ​​to come into contact with the lubricating oil Lb remains in each of the machine chambers R2.With this configuration, even if the pump 1 (in the axial direction of the rotating shaft 4) is tilted to the maximum tilt angle relative to the horizontal direction that is greater than the valve closing angle (the tilt angle changes to the maximum tilt angle), the valve V closes when an amount of lubricating oil Lb remains inside each of the multiple machine chambers R2 such that each of the multiple bearings 5 ​​comes into contact with the lubricating oil Lb. In other words, even if the pump 1 (in the axial direction of the rotating shaft 4) is tilted to the maximum tilt angle relative to the horizontal direction, each of the multiple bearings 5 ​​arranged in each of the multiple machine chambers R2 comes into contact with the lubricating oil Lb. Therefore, the movement of the lubricating oil Lb is suppressed when the pump 1 (in the axial direction of the rotating shaft 4) is tilted relative to the horizontal direction, and damage to the bearings 5 ​​is prevented.

[0077] According to the above description, the partition wall 23 has a gas communication hole H2. The gas communication hole H2 connects adjacent machine chambers R2 to each other among the multiple machine chambers R2. In the vertical direction, the gas communication hole H2 is located above the liquid level of the lubricating oil Lb. With this configuration, the multiple machine chambers R2 are connected to each other via the gas communication holes H2 located above the liquid level of the lubricating oil Lb. Therefore, gas (e.g., air) in the gas phase within the machine chambers R2 moves through each of the multiple machine chambers R2 via the gas communication hole H2. That is, the volume of the space within the machine chamber R2 is larger than the volume of the space in a configuration in which the machine chambers are not connected to each other. Therefore, when the connecting member 8 reciprocates in the front-rear direction, the volumetric change rate of the space within the machine chamber R2 is smaller than the volumetric change rate in the same configuration. Therefore, the internal pressure of the machine chamber R2 is unlikely to fluctuate significantly. In other words, the change in the internal pressure of the machinery chamber R2 is suppressed, and as a result, the lifespan of the components (for example, sealing members) arranged in the machinery chamber R2 is less likely to be shortened.

[0078] As explained above, the rotating shaft 4 includes the first to fourth individual rotating shafts 4a to 4d. The first to fourth individual rotating shafts 4a to 4d correspond to the pump units PU, respectively. The first to fourth individual rotating shafts 4a to 4d are arranged side by side in the axial direction to form the rotating shaft 4. The pump 1 includes a coupling 6. The coupling 6 connects adjacent individual rotating shafts (the first to fourth individual rotating shafts 4a to 4d) to each other in the axial direction. The partition wall 23 includes a coupling chamber R3 (R3a, R3b). The coupling chamber R3 houses the coupling 6. The coupling chamber R3 is arranged between adjacent machine chambers R2. The direction in which the motor 3 is disposed relative to the rotating shaft 4 (the direction in which one end of the rotating shaft 4 faces in the axial direction) is the leftward direction. The opposite direction to the leftward direction (the direction in which the other end of the rotating shaft 4 faces in the axial direction) is the rightward direction. The liquid communication hole H1 includes a first liquid communication hole H1a, a second liquid communication hole H1b, a third liquid communication hole H1c, and a fourth liquid communication hole H1d. The first liquid communication hole H1a connects the coupling chamber R3a to the machine chamber R2a located to the left of the coupling chamber R3a. The second liquid communication hole H1b connects the coupling chamber R3a to the machine chamber R2b located to the right of the coupling chamber R3a. The third liquid communication hole H1c connects the coupling chamber R3b to the machine chamber Rb located to the left of the coupling chamber R3b. The fourth liquid communication hole H1d connects the coupling chamber R3b to the machine chamber R2c located to the right of the coupling chamber R3b. According to this configuration, some of the individual rotating shafts (first individual rotating shaft 4a to third individual rotating shaft 4c) connected to one another via the coupling 6 can be removed as needed. Therefore, if one of the pump units PU among the plurality of pump units PU is damaged, that pump unit PU can be removed together with some of the individual rotating shafts (first individual rotating shaft 4a to third individual rotating shaft 4c). This improves the maintainability of the pump 1.Furthermore, when the tilt angle is changed to the maximum tilt angle, the amount of lubricating oil Lb stored inside the machine chamber R2 in which the highest bearing 5 of the multiple bearings 5 ​​is located is maintained at an amount that allows the bearing 5 to come into contact with the lubricating oil Lb. Furthermore, the coupling chamber R3 is located between adjacent machine chambers R2. Therefore, the amount of lubricating oil Lb stored inside the coupling chamber R3 is also maintained at an amount that allows the coupling 6 to come into contact with the lubricating oil Lb. Therefore, even if the pump 1 (axial direction of the rotating shaft 4) is tilted to the maximum tilt angle with respect to the horizontal direction, which is greater than the valve closing angle (the tilt angle has changed to the maximum tilt angle), the coupling 6 housed in the coupling chamber R3 can also come into contact with the lubricating oil Lb.

[0079] As explained above, the valve V comprises a valve element V1 and two valve seat surfaces V2. The valve element V1 is movable axially within the liquid communication hole H1. The two valve seat surfaces V2 are arranged in the liquid communication hole H1 so as to sandwich the valve element V1 in the axial direction. When the axial direction of the rotating shaft 4 is tilted to the valve closing angle, the valve element V1 abuts against the valve seat surfaces V2 and closes the liquid communication hole H1. With this configuration, movement of the lubricating oil Lb is suppressed when the pump 1 (axial direction of the rotating shaft 4) is tilted relative to the horizontal direction, preventing damage to the bearing 5.

[0080] According to the above explanation, the specific gravity of the valve disc V1 is greater than the specific gravity of the lubricating oil Lb. The valve disc V1 is housed in the corresponding liquid communication hole H1 and moves axially within the liquid communication hole H1 according to the angle of inclination. In the vertical direction, the liquid communication hole H1 is positioned below the liquid level of the lubricating oil Lb. In other words, the liquid communication hole H1 is immersed in the lubricating oil Lb. With this configuration, even when the valve disc V1 is immersed in the lubricating oil Lb, it can move within the liquid communication hole H1 according to the angle of inclination. Furthermore, even if a flow of lubricating oil Lb occurs that hinders the movement of the valve disc V1 during operation of the pump 1, the valve disc V1 can move against the flow.

[0081] ●Variations● Next, modified examples of the present pump will be described, focusing on the differences from the embodiment of the present pump described above (hereinafter referred to as the "first embodiment"). In the following description, for convenience of explanation, the same components as those in the first embodiment and components having the same functions as those in the first embodiment are given the same reference numerals as those in the first embodiment, unless otherwise specified, and their explanation will be omitted. In addition, in the following modified examples, reference will be made to Figures 1 to 4 as appropriate.

[0082] FIG. 9 is an enlarged schematic view of the vicinity of the valve V of the pump 1A, showing a modification of the pump 1. 9, (a) shows the state of the valve V when the axial direction of the rotating shaft 4 is parallel to the horizontal. (b) shows the state of the valve V when the axial direction of the rotating shaft 4 is tilted counterclockwise at an angle of θ3° with respect to the horizontal when viewed from the rear. (c) shows the state of the valve V when the axial direction of the rotating shaft 4 is tilted clockwise at an angle of θ3° with respect to the horizontal when viewed from the rear.

[0083] When the axial direction of the rotating shaft 4 is tilted to the maximum tilt angle greater than the valve closing angle (when the tilt angle changes to the maximum tilt angle), the machine chambers R2 most likely to experience a shortage of lubricant Lb are the left and right machine chambers R2a, R2c. Therefore, it is preferable that the movement of lubricant Lb from the lubricant oil reservoirs 24 in the left and right machine chambers R2a, R2c to the adjacent lubricant oil reservoirs 24 be more limited than the movement of lubricant Lb between the other lubricant oil reservoirs 24.

[0084] In this modification, the shape of the valve seat surface V2 arranged in the liquid communication hole H1 differs from that of the first embodiment.

[0085] Here, the multiple valve bodies V1 include multiple (six) specific valve bodies V1a. The specific valve body V1a is the valve body arranged on the leftmost side (closest to the machine chamber R2a) among the multiple valve bodies V1. The specific valve body V1a is accommodated in the corresponding first liquid communication hole H1a. The specific valve body V1a is an example of the first valve body in the present invention. The multiple valve seat surfaces V2 include multiple (six) first valve seat surfaces V2a and multiple (six) second valve seat surfaces V2b. The first valve seat surface V2a is arranged on the leftmost side (closest to the machine chamber R2a) among the multiple valve seat surfaces V2. The first valve seat surface V2a and the second valve seat surface V2b are arranged in the corresponding first liquid communication hole H1a so as to sandwich the specific valve body V1a. The second valve seat surface V2b is arranged on the right side of the first valve seat surface V2a. In a rear view, the inclination angle θx of the first valve seating surface V2a relative to the axial direction is larger than the inclination angle θy of the second valve seating surface V2b relative to the axial direction. That is, the shape of the first valve seating surface V2a is different from the shape of the second valve seating surface V2b.

[0086] As described above, in the first embodiment, when the tilt angle is equal to or greater than the valve closing angle ("angle θ2°"), the valve element V1 moves within the liquid communication hole H1. At this time, the valve element V1 abuts against the valve seat surface V2, blocking the liquid communication hole H1. In other words, the valve V is closed.

[0087] According to the configuration of the modified example, when the axial direction of the rotating shaft 4 is tilted counterclockwise by an angle θ3° (e.g., 2°) with respect to the horizontal direction as viewed from the rear, the specific valve element V1a moves leftward within the liquid communication hole H1. At this time, the specific valve element V1a abuts against the first valve seat surface V2a and does not block the liquid communication hole H1 (see FIG. 9(b)). On the other hand, when the axial direction of the rotating shaft 4 is tilted clockwise by an angle θ3° with respect to the horizontal direction as viewed from the rear, the specific valve element V1a moves rightward within the liquid communication hole H1. At this time, the specific valve element V1a abuts against the second valve seat surface V2b and blocks the liquid communication hole H1 (see FIG. 9(c)). In other words, the valve closing angle when the axial direction of the rotating shaft 4 is tilted clockwise with respect to the horizontal direction is an angle θ3°. The valve closing angle when the axial direction of the rotating shaft 4 tilts counterclockwise with respect to the horizontal is greater than the angle θ3°. In other words, the valve closing angle when the specific valve element V1a moves leftward is greater than the valve closing angle when the specific valve element V1a moves rightward. When viewed from the rear, the amount of lubricating oil Lb stored in the machine chamber R2a that moves to the machine chamber R2b when the axial direction of the rotating shaft 4 continues to tilt clockwise with respect to the horizontal is less than the amount of lubricating oil Lb stored in the machine chamber R2b that moves to the machine chamber R2a when the axial direction of the rotating shaft 4 continues to tilt counterclockwise with respect to the horizontal. In other words, the amount of lubricating oil Lb stored in the machine chamber R2a is less likely to decrease than the amount of lubricating oil Lb stored in the other machine chambers R2b and R2c.

[0088] ●Other embodiments● In the present invention, the pump 1 does not necessarily have to include the coupling chamber R3 and the coupling 6. In this case, the rotating shaft 4 is not divided into multiple individual rotating shafts (first individual rotating shaft 4a to third individual rotating shaft 4c) as in the first embodiment, but is composed of a single shaft member. Furthermore, since there is no longer a need for two liquid communication holes H1 to communicate between the two machine chambers R via the coupling chamber R3 as in the first embodiment, one liquid communication hole H1 communicates between the two machine chambers R. In other words, the number of liquid communication holes H1 is half compared to when the pump 1 includes the coupling chamber R3 and the coupling 6. The same applies to the number of gas communication holes H2.

[0089] In the modified example described above, the specific valve element V1a is the one located on the leftmost side (closest to the machine chamber R2a) of the multiple valve elements V1. Alternatively, the specific valve element V1a may be the one located on the rightmost side (closest to the machine chamber R2c) of the multiple valve elements V1. In this case, the specific valve element V1a is accommodated in the corresponding fourth liquid communication hole H1d. The first valve seat surface V2a is located on the rightmost side (closest to the machine chamber R2d) of the multiple valve seat surfaces V2. The first valve seat surface V2a and the second valve seat surface V2b are located in the corresponding fourth liquid communication hole H1d so as to sandwich the specific valve element V1a. The second valve seat surface V2b is located on the left side of the first valve seat surface V2a. In a rear view, the inclination angle θx of the first valve seat surface V2a relative to the axial direction is larger than the inclination angle θy of the second valve seat surface V2b relative to the axial direction. According to this configuration, the valve closing angle when the specific valve element V1a moves rightward is larger than the valve closing angle when the specific valve element V1a moves leftward. In a rear view, the amount of lubricating oil Lb stored in the machine chamber R2c moving to the machine chamber R2b when the axial direction of the rotating shaft 4 continues to tilt counterclockwise relative to the horizontal is smaller than the amount of lubricating oil Lb stored in the machine chamber R2b moving to the machine chamber R2c when the axial direction of the rotating shaft 4 continues to tilt clockwise relative to the horizontal. In other words, the amount of lubricating oil Lb stored in the machine chamber R2c is less likely to decrease than the amount of lubricating oil Lb stored in the other machine chambers R2a and R2b.

[0090] Furthermore, in the present invention, the pump 1 is not limited to a diaphragm pump, and may be, for example, a piston pump or a plunger pump.

[0091] Furthermore, in the present invention, the number of pump units PU (pump chamber R1, plunger 9, and diaphragm 10) and transmission mechanisms TM (connecting rod 7 and coupling member 8) is not limited to three. That is, for example, the number of pump units PU (pump chamber R1, plunger 9, and diaphragm 10) and transmission mechanisms TM (connecting rod 7 and coupling member 8) may be two or four or more. In this case, the number of each component of the pump 1 is determined appropriately depending on the number of pump units PU and transmission mechanisms TM.

[0092] Furthermore, in the present invention, the number of machine chambers R2 is not limited to 3. That is, the number of machine chambers R2 may be 2 or 4 or more. In this case, the number of coupling chambers R3 arranged between multiple machine chambers R2 is determined appropriately depending on the number of machine chambers R2.

[0093] Furthermore, the number of liquid communication holes H1 and gas communication holes H2 is not limited to 24. That is, for example, the number of liquid communication holes H1 and gas communication holes H2 may be any number that allows the lubricating oil Lb to move inside each chamber (machine chamber R2 and coupling chamber R3) in the parallel state, and that leaves a sufficient amount of lubricating oil Lb stored inside each chamber (machine chamber R2 and coupling chamber R3) in the tilted state.

[0094] Furthermore, in the present invention, the valve closing angle is not limited to "angle θ2° (e.g., approximately 2° to 5°)." That is, for example, the valve closing angle may be any angle such that, after the valve V is closed, the axial direction of the rotating shaft 4 is tilted to the maximum tilt angle (22.5°) relative to the horizontal direction that is greater than the valve closing angle, so that an amount of lubricating oil Lb that brings each of the bearings 5 ​​into contact with the lubricating oil Lb remains in each of the multiple machine chambers R2, and is determined appropriately depending on the design of the pump 1 (e.g., the oil level relative to the rotating shaft 4, the amount of oil in one machine chamber R2, etc.).

[0095] Furthermore, in the present invention, the rotating shaft 4 may be indirectly connected to the motor 3. That is, for example, the rotating shaft 4 may be connected to the motor 3 via a known intersecting axis gear or a known reducer.

[0096] ●Embodiments of the present invention● Next, embodiments of the present invention that can be understood from the above-described embodiments will be described below, using the terms and symbols described in the embodiments.

[0097] A first embodiment of the present invention is a pump system including a plurality of pump units (e.g., pump unit PU) that suck and discharge a treated liquid (e.g., treated liquid W), a motor (e.g., motor 3) that generates power required for the operation of each of the plurality of pump units, a rotating shaft (e.g., rotating shaft 4) connected to the motor, a plurality of bearings (e.g., bearings 5a to 5f) that support the rotating shaft, and lubricating oil (e.g., lubricating oil Lb) used to lubricate each of the plurality of bearings. and a housing (for example, housing 2) that houses the rotary shaft and the plurality of transmission mechanisms, and the housing is provided with a plurality of machine chambers (for example, machine chambers 2a, 2b, 2c) that house the corresponding transmission mechanisms, and partition walls (for example, partition walls 23a, 23b) that separate the plurality of machine chambers, and the plurality of machine chambers are arranged side by side along the axial direction of the rotary shaft, and the partition walls are spaced apart from each other in the axial direction. The partition wall is disposed between the machine chambers, and the partition wall is provided with a communication hole (e.g., a liquid communication hole H1) that communicates between adjacent machine chambers among the plurality of machine chambers, and a valve (e.g., a valve V) that is disposed in the communication hole, and the plurality of bearings are disposed at both ends of the corresponding machine chamber in the axial direction, the lubricating oil is stored inside each of the plurality of machine chambers, the communication hole is disposed below the liquid level of the lubricating oil in the vertical direction, and the axial direction is parallel to the horizontal direction. In a reciprocating pump (e.g., pump 1, 1A), each of the plurality of bearings is in contact with the lubricating oil at a certain time, and the valve closes when the tilt angle of the axial direction with respect to the horizontal direction is equal to or greater than a valve closing angle, and opens when the tilt angle is less than the valve closing angle, and the valve closing angle is an angle at which, after the valve is closed, the rotating shaft is tilted to a predetermined tilt angle greater than the valve closing angle, and an amount of lubricating oil that causes each of the plurality of bearings to come into contact with the lubricating oil remains in each of the machine chambers. According to this configuration, movement of lubricating oil is suppressed when the pump (axial direction of the rotary shaft) is tilted relative to the horizontal direction, and damage to the bearings is prevented.

[0098] A second embodiment of the present invention is a reciprocating pump according to the first embodiment, wherein the partition wall has a gas communication hole (e.g., gas communication hole H2) that connects adjacent machine chambers among the plurality of machine chambers, and the gas communication hole is positioned above the liquid surface of the lubricating oil in the vertical direction. According to this configuration, the life of the members (for example, sealing members) arranged in the machine chamber is unlikely to be shortened.

[0099] A third embodiment of the present invention is the first or second embodiment, wherein the rotating shaft comprises a plurality of individual rotating shafts (for example, a first individual rotating shaft 4a, a second individual rotating shaft 4b, and a third individual rotating shaft 4c) corresponding to each of the plurality of pump units, and the plurality of individual rotating shafts are arranged side by side in the axial direction to form the rotating shaft, and have couplings (for example, couplings 6a, 6b) that connect adjacent individual rotating shafts to each other in the axial direction, and the partition wall comprises coupling chambers (for example, coupling chambers R3a, R3b) that accommodate the couplings, and the coupling chambers connect adjacent individual rotating shafts to each other in the axial direction. The reciprocating pump is disposed between machine chambers, and in the axial direction, one end of the rotating shaft faces a first direction (e.g., leftward), and the other end of the rotating shaft faces a second direction (e.g., rightward), and the communication holes include first communication holes (e.g., first liquid communication hole H1a and third liquid communication hole H1c) that connect the coupling chamber to the machine chamber on the first direction side of the coupling chamber, and second communication holes (e.g., second liquid communication hole H1b and fourth liquid communication hole H1d) that connect the coupling chamber to the machine chamber on the second direction side of the coupling chamber. According to this configuration, the coupling housed in the coupling chamber can come into contact with the lubricating oil.

[0100] A fourth embodiment of the present invention is a reciprocating pump in which, in the first embodiment, the valve comprises a valve body (e.g., valve body V1) that is movable along the axial direction within the communicating hole, and two valve seat surfaces (e.g., valve seat surface V2) that are arranged to sandwich the valve body in the axial direction, and when the rotation axis is inclined to the valve closing angle, the valve body abuts against the valve seat surfaces to block the communicating hole. According to this configuration, movement of lubricating oil is suppressed when the pump (in the axial direction of the rotary shaft) is tilted relative to the horizontal direction, and damage to the bearings is prevented.

[0101] A fifth embodiment of the present invention is a reciprocating pump (e.g., this pump 1A) in the fourth embodiment, wherein, in the axial direction, the direction in which one end of the rotating shaft is facing is a first direction (e.g., a left direction), and the direction in which the other end of the rotating shaft is facing is a second direction (e.g., a right direction), the multiple machine chambers include a first machine chamber (e.g., machine chamber R2a) that is located closest to the first direction among the multiple machine chambers, and a second machine chamber (e.g., machine chamber R2b) that is located closer to the second direction than the first machine chamber and adjacent to the first machine chamber, the multiple valve bodies include a first valve body (e.g., a specific valve body V1a) that is located closest to the first machine chamber among the multiple valve bodies, and the valve closing angle when the first valve body moves in the first direction is larger than the valve closing angle when the first valve body moves in the second direction. With this configuration, the amount of lubricating oil stored in the machines at both the left and right ends of the multiple machine chambers is unlikely to decrease.

[0102] A sixth embodiment of the present invention is the reciprocating pump of the fourth embodiment, wherein the specific gravity of the valve body is greater than the specific gravity of the lubricating oil. With this configuration, even if a flow of lubricating oil occurs that hinders the movement of the valve element during operation of the pump, the valve element can move against the flow. [Explanation of symbols]

[0103] 1 Reciprocating Pump 2. Case R2 Machine room R2a Machine room R2b Machine room R2c machine room 23 Bulkhead 23a Bulkhead 23b Bulkhead H1 Liquid communication hole H1a 1st liquid communication hole H1b 2nd liquid communication hole H1c 3rd liquid communication hole H1d 4th liquid communication hole H2 gas communication hole H2a First gas communication hole H2b Second gas communication hole H2c Third gas communication hole H2d 4th gas communication hole V-valve V1 Valve body V2 valve seat surface R3 Coupling chamber R3a Coupling Room R3b Coupling Room 3 motors 4 rotation axes 4a First individual rotation axis 4b Second individual rotation axis 4c Third individual rotation axis 5. Bearings 5a Bearing 5b Bearing 5c bearing 5d bearing 5e bearing 5f bearing 6 Coupling 6a Coupling 6b Coupling Lb lubricant PU pump unit TM transmission mechanism W Handling fluid 1A reciprocating pump V1a specific valve body

Claims

1. a plurality of pump units that suck and discharge the pumped liquid; a motor that generates power necessary for the operation of each of the plurality of pump units; a rotating shaft connected to the motor; a plurality of bearings supporting the rotating shaft; a lubricating oil used to lubricate each of the plurality of bearings; a plurality of transmission mechanisms that transmit the power generated by the motor to the corresponding pump units via the rotary shaft; a housing that accommodates the rotary shaft and the plurality of transmission mechanisms; and The housing includes: a plurality of machine rooms accommodating the corresponding transmission mechanisms; Partition walls that separate the plurality of machine rooms; With The plurality of machine chambers are arranged side by side along the axial direction of the rotation shaft, The partition wall is disposed between adjacent machine chambers in the axial direction, The partition wall is a communication hole that connects adjacent machine chambers to each other among the plurality of machine chambers; a valve disposed in the communication hole; With In the axial direction, each of the plurality of bearings is disposed at both ends of the corresponding machine chamber, The lubricating oil is stored inside each of the plurality of machine chambers, The communication hole is The lubricating oil supply pipe is disposed below the liquid level of the lubricating oil in the vertical direction. When the axial direction is parallel to the horizontal direction, each of the plurality of bearings is in contact with the lubricating oil, The valve is When the inclination angle of the axial direction with respect to the horizontal direction is equal to or greater than the valve closing angle, the valve is closed, When the tilt angle is less than the valve closing angle, the valve opens, The valve closing angle is the angle at which, when the axial direction is inclined to a predetermined angle greater than the valve closing angle with respect to the horizontal direction after the valve is closed, the amount of lubricating oil remaining in each of the machine chambers is such that each of the plurality of bearings comes into contact with the lubricating oil. Reciprocating pump.

2. The partition wall is a gas communication hole that connects adjacent machine chambers among the plurality of machine chambers to each other; With In the vertical direction, the gas communication hole is disposed above the liquid surface of the lubricating oil.

2. The reciprocating pump according to claim 1.

3. The rotation axis is a plurality of individual rotating shafts corresponding to the plurality of pump units, respectively; With The plurality of individual rotation shafts are arranged side by side in the axial direction to form the rotation shaft, a coupling that connects adjacent individual rotation shafts to each other in the axial direction; and The partition wall is a coupling chamber for accommodating the coupling; With The coupling chamber is disposed between the adjacent machine chambers, In the axial direction, a direction in which one end of the rotation shaft is directed is a first direction, and a direction in which the other end of the rotation shaft is directed is a second direction, The communication hole is a first communication hole that communicates the coupling chamber with the machine chamber on the first direction side of the coupling chamber; a second communication hole that communicates the coupling chamber with the machine chamber on the second direction side of the coupling chamber; Equipped with 3. The reciprocating pump according to claim 1 or 2.

4. The valve is a valve body movable in the axial direction within the communication hole; two valve seat surfaces arranged to sandwich the valve body in the axial direction; With When the axial direction is inclined to the horizontal direction up to the valve closing angle, The valve body is abutting against the valve seat surface to close the communication hole; 2. The reciprocating pump according to claim 1.

5. In the axial direction, a direction in which one end of the rotation shaft is directed is a first direction, and a direction in which the other end of the rotation shaft is directed is a second direction, The plurality of machine rooms include: a first machine room arranged closest to the first direction among the plurality of machine rooms; a second machine room disposed on the second direction side of the first machine room and adjacent to the first machine room; Including, The plurality of valve bodies a first valve body disposed closest to the first machine chamber among the plurality of valve bodies; Including, The valve closing angle when the first valve body moves in the first direction is larger than the valve closing angle when the first valve body moves in the second direction.

5. The reciprocating pump according to claim 4.

6. The specific gravity of the valve body is greater than the specific gravity of the lubricating oil.

5. The reciprocating pump according to claim 4.

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