Abstract:
An electromagnetic switching valve, for which the maximum opening is set to be small, is disposed on piping between a lift cylinder and a hydraulic pump motor. A pilot check valve, for which the maximum opening is set to be larger than the electromagnetic switching valve, is disposed on piping, different from the piping, between the lift cylinder and the hydraulic pump motor. In addition, during lowering operations, first, the electromagnetic switching valve is opened, and then after the same is opened, the pilot check valve is opened after a prescribed time has passed. Thus, the shock generated when lowering an object to be raised/lowered is reduced and a fork is operated quickly.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
       [0001]    This is a National Stage of International Application No. PCT/JP2012/076915 filed Oct. 18, 2012, the contents of which are incorporated herein by reference in its entirety. 
     
    
     TECHNICAL FIELD 
       [0002]    The present invention relates to a lifting device that includes a hydraulic cylinder used for lifting and lowering and hydraulically drives the hydraulic cylinder to lift and lower a lifting material. 
       BACKGROUND ART 
       [0003]    A lifting device may hydraulically drive a hydraulic cylinder to lift and lower a lifting material. For example, patent document 1 describes such a known lifting device that is used for a forklift. A lifting device for a forklift lifts and lowers a fork (material handler), which serves as a lifting material, by supplying and discharging hydraulic oil to and from a hydraulic cylinder. This type of a lifting device includes a switch valve that controls the hydraulic oil flowing to a hydraulic pipe arranged between a hydraulic cylinder and the hydraulic pump. The fork is lifted, lowered, or stopped by controlling the opening and closing of the switch valve. 
         [0004]    However, the switch valve may have different pressures at an inflow side and an outflow side of the hydraulic oil. Under this condition, if the lifting device for a forklift opens the switch valve to lower the fork, a shock would occur when the hydraulic oil starts flowing. Such a shock leads to unstable operation of the fork, which would move a carried cargo. 
         [0005]    The lifting device of patent document 1 includes a means for solving the above problem. More specifically, the lifting device of patent document 1 temporarily activates the hydraulic pump to lift the fork when starting a lowering operation to decrease the pressure difference. 
       PRIOR ART DOCUMENT 
     Patent Document 
       [0006]    Patent Document 1: Japanese Laid-Open Patent Publication No. 2008-7258 
       SUMMARY OF THE INVENTION 
       [0007]    When starting the present lowering operation, the lifting device of patent document 1 determines, from the time elapsed from when the preceding lowering operation ended and the pressure of the cylinder, how fast and how long the hydraulic pump produces rotation in a lifting direction. The lifting device of patent document 1 may obtain a value taken when the cylinder pressure is pulsating. In such a case, the increased pressure may be excessive or insufficient. When the increase in the pressure is excessive, the hydraulic cylinder performs a lifting operation. From this condition, the lowering operation is performed. This generates a time lag between when the lowering operation is instructed and when the lowering operation actually starts. When the increase in the pressure is insufficient, the hydraulic cylinder performs a lowering operation without decreasing the pressure difference. This generates a shock when the hydraulic oil starts flowing. 
         [0008]    It is an object of the present invention to provide a lifting device that may be readily operated and reduces the shock that may occur when a lifting material is lowered. 
         [0009]    To achieve the above object, one aspect of the present invention is a lifting device that lifts and lowers a lifting material by supplying and discharging hydraulic oil to and from a hydraulic cylinder. The lifting device includes a hydraulic pump that supplies the hydraulic oil to the hydraulic cylinder, a first oil passage that connects the hydraulic cylinder and the hydraulic pump, a second oil passage that connects the hydraulic cylinder and the hydraulic pump, and an opening-closing unit that opens and closes the first oil passage and the second oil passage. The first oil passage has a maximum oil passage area that is smaller than a maximum oil passage area of the second oil passage. The first oil passage includes a first portion between the hydraulic cylinder and the opening-closing unit and a second portion between the opening-closing unit and the hydraulic pump. The opening-closing unit allows the hydraulic oil to flow through the first oil passage when the lifting material is lowered. After the first oil passage opens, the opening-closing unit allows the hydraulic oil to flow through the second oil passage when a first pressure difference between the first portion and the second portion decreases to a predetermined pressure difference or less. 
         [0010]    In the above structure, the first oil passage, which has the small maximum oil passage area, connects first during a lowering operation. Since the maximum oil passage area of the first oil passage is small, a flow rate of the hydraulic oil flowing to the oil passage is limited. Thus, the hydraulic oil does not suddenly start flowing. Connection of the first oil passage decreases the pressure difference between the hydraulic cylinder and the hydraulic pump (first pressure difference between the first portion and the second portion). After the first oil passage opens, when the second oil passage, which has the large maximum oil passage area, opens, the pressure difference has been already decreased between the hydraulic cylinder and the hydraulic pump. This limits generation of a shock even when the hydraulic oil suddenly flows, thereby decreasing a shock that may occur when lowering the lifting material. Additionally, when the lowering operation starts, the hydraulic pump is not controlled to perform lifting operation. This minimizes the time lag from when a lowering operation is instructed to when the lowering operation is actually performed. Consequently, the lifting material may be promptly operated. 
         [0011]    Preferably, the opening-closing unit includes a first direction control valve arranged in the first oil passage and a second direction control valve arranged in the second oil passage. The first direction control valve switches a flow direction of the hydraulic oil in the first oil passage. The second direction control valve switches a flow direction of the hydraulic oil in the second oil passage. The maximum oil passage area of the first oil passage is determined by a maximum open degree of the first direction control valve. The maximum oil passage area of the second oil passage is determined by a maximum open degree of the second direction control valve. The maximum open degree of the first direction control valve is smaller than the maximum open degree of the second direction control valve. 
         [0012]    In the above structure, the opening-closing unit includes the first direction control valve, which has the small maximum open degree, and the second direction control valve. The maximum open degree of the second direction control valve is larger than the maximum open degree of the first direction control valve. After the first direction control valve opens, the second direction control valve opens. Thus, a simple structure may be used to promptly operate the lifting operation while decreasing a shock that may occur when lowering the lifting material. 
         [0013]    Preferably, the hydraulic oil flows from the hydraulic cylinder toward the hydraulic pump through the first and second oil passages when the first direction control valve and the second direction control valve open, thereby causing the hydraulic oil to function as driving power used for driving the hydraulic pump as a hydraulic motor so that the hydraulic motor performs a regeneration operation. 
         [0014]    In the above structure, electric energy may be efficiently used resulting from the regeneration operation of the lowering operation. The maximum open degree of the second direction control valve is large. Thus, the pressure drop is small when the hydraulic oil passes through the second direction control valve. This provides a sufficient torque used for rotating the hydraulic pump as the hydraulic motor. Consequently, electric energy may be efficiently obtained from the regeneration operation. 
         [0015]    Preferably, the maximum open degree of the second direction control valve is set to be in a range of 20 to 50 times larger than the maximum open degree of the first direction control valve. 
         [0016]    In the above structure, the difference in the maximum open degree between the first direction control valve and the second direction control valve is large. This allows a prompt operation while decreasing a shock that may occur when lowering the lifting material by controlling the timing for opening the first direction control valve and the second direction control valve without proportionally controlling open degrees of the valves. 
         [0017]    Preferably, the lifting device further includes a measurement unit that measures a time elapsed from when the first direction control valve opens. The opening-closing unit opens the second direction control valve when the elapsed time reaches a predetermined time. 
         [0018]    In the above structure, the timing for opening the second direction control valve is managed based on time. Thus, the control may be simplified. 
         [0019]    Preferably, the lifting device further includes a third oil passage, through which the hydraulic oil that has passed through the second direction control valve flows, and a switch valve arranged in the third oil passage. The first direction control valve is an electromagnetic switch valve. The second direction control valve is a pilot check valve including a valve body accommodated in the second direction control valve and a throttle oil passage formed in the valve body. The opening-closing unit is configured to open the switch valve. When the switch valve opens, the hydraulic oil is discharged from the hydraulic cylinder to the third oil passage through the throttle oil passage, which generates a second pressure difference between an inflow side and an outflow side of the throttle oil passage. The valve body moves in a direction in which the second oil passage opens in accordance with the second pressure difference. 
         [0020]    In the above structure, the electromagnetic switch valve of the third oil passage is a means for applying the pilot pressure to the pilot check valve. This limits an enlargement of the device and an increase in costs compared to when an electromagnetic switch valve having a large maximum open degree is employed instead of the pilot check valve. 
       Effects of the Invention 
       [0021]    The present invention performs a prompt operation while decreasing a shock that may occur when a lifting material is lowered. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0022]      FIG. 1  is a circuit diagram of a first embodiment of a lifting device. 
           [0023]      FIG. 2  is a schematic view schematically showing the internal structure of a pilot check valve. 
           [0024]      FIG. 3  is a flowchart showing the procedures of operations. 
           [0025]      FIG. 4  is a circuit diagram of a second embodiment of a lifting device. 
           [0026]      FIG. 5  is a circuit diagram of a third embodiment of a lifting device. 
           [0027]      FIG. 6  is a circuit diagram of a fourth embodiment of a lifting device. 
       
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
     First Embodiment 
       [0028]    A first embodiment of a lifting device that includes a lift cylinder lifting and lowering a fork of a forklift according to the present invention will now be described with reference to  FIGS. 1 to 3 . 
         [0029]    A fork F is arranged at the front of a forklift and serves as a material handler (lifting material). When a lift lever L arranged in a cab is operated, a lift cylinder  10 , which serves as a hydraulic cylinder, is extended or retracted to lift and lower the fork F. 
         [0030]    A hydraulic control mechanism used for operating the lift cylinder  10  of the present embodiment will now be described with reference to  FIG. 1 . 
         [0031]    A main pipe K, which has a closed circuit structure, is connected to a hydraulic pump motor  11 , which functions as a hydraulic pump and a hydraulic motor. The main pipe K is also connected to a pipe K 1 , which serves as a first oil passage. The pipe K 1  forms a passage through which the hydraulic oil is supplied to and discharged from the lift cylinder  10  and is connected to a bottom chamber  10   a  of the lift cylinder  10 . The pipe K 1  connects the lift cylinder  10  and the hydraulic pump motor  11 . The hydraulic pump motor  11  is configured to be capable of producing rotation in two directions. The main pipe K is connected to transmission openings  11   a ,  11   b  of the hydraulic pump motor  11 . The transmission openings  11   a ,  11   b  each serve as an inlet or outlet in accordance with the flow direction of the hydraulic oil. 
         [0032]    The hydraulic pump motor  11  is connected to a lift motor  12  (rotational electric device), which functions as an electric motor and an electric generator. The lift motor  12  functions as an electric motor when a coil of a stator (not shown) is energized to rotate a rotor. The lift motor  12  functions as an electric generator when rotation of the rotor generates power in the coil of the stator. The lift motor  12  of the present embodiment functions as an electric motor when activating the hydraulic pump motor  11  as a hydraulic pump, and as an electric generator when activating the hydraulic pump motor  11  as a hydraulic motor. 
         [0033]    Additionally, the main pipe K is connected to a supply pipe K 2 . When the lift cylinder  10  performs a lifting operation, the hydraulic pump motor  11  is activated to draw the hydraulic oil from an oil tank  13  and deliver the hydraulic oil through the supply pipe K 2 . The supply pipe K 2  includes a check valve  14  (non-return valve) that prevents reverse flow from the main pipe K to the oil tank  13 . The main pipe K is also connected to a discharge pipe K 3 . When the lift cylinder  10  performs a lowering operation, the hydraulic pump motor  11  is activated to return the hydraulic oil to the oil tank  13  through the discharge pipe K 3 . The discharge pipe K 3  includes a check valve  15  (non-return valve) that prevents reverse flow from the oil tank  13  to the main pipe K. The discharge pipe K 3  includes a filter  16  between the oil tank  13  and the check valve  15 . 
         [0034]    Additionally, the main pipe K includes a check valve  17  (non-return valve) that prevents reverse flow from the main pipe K, which is connected to the transmission opening  11   a  of the hydraulic pump motor  11 , to the main pipe K, which is connected to the transmission opening  11   b  of the hydraulic pump motor  11 . The check valve  17  is arranged in an oil passage between the transmission opening  11   a , which may serve as the outlet of the hydraulic pump motor  11 , and the oil tank  13 , which stores the hydraulic oil. The check valve  17  allows the hydraulic oil to flow from an oil passage located toward the oil tank  13  from the check valve  17  to the main pipe K located toward the transmission opening  11   b  of the hydraulic pump motor  11  from the check valve  17 . The main pipe K also includes a relief valve  18 , which prevents an increase in the pressure. 
         [0035]    The pipe K 1 , which is connected to the bottom chamber  10   a  of the lift cylinder  10 , includes an electromagnetic switch valve  19 . The electromagnetic switch valve  19  serves as a first direction control valve that switches a flow direction of the hydraulic oil flowing in the first oil passage. The electromagnetic switch valve  19  may be shifted between two positions, namely, a first position  19   a  and a second position  19   b . When a solenoid is not excited, the electromagnetic switch valve  19  of the present embodiment is set at the first position  19   a  and allows the hydraulic oil to flow from the hydraulic pump motor  11  to the lift cylinder  10 . When the solenoid is excited, the electromagnetic switch valve  19  of the present embodiment is set at the second position  19   b  and allows the hydraulic oil to bidirectionally flow between the hydraulic pump motor  11  and the lift cylinder  10 . The electromagnetic switch valve  19  of the present embodiment is an on-off valve, which adjusts an open degree in accordance with the excitement (on) and non-excitement (off) of the solenoid. Thus, the electromagnetic switch valve  19  of the present embodiment differs from an electromagnetic proportional valve capable of adjusting the open degree in a non-stepped manner. The electromagnetic switch valve  19  of the present embodiment forms an opening-closing unit that opens and closes the pipe K 1 , which serves as the first oil passage. 
         [0036]    Additionally, the present embodiment includes a pipe K 4 , which serves as a second oil passage, arranged separately from the pipe K 1 , which serves as the first oil passage. The pipe K 4  forms a passage through which the hydraulic oil is supplied to and discharged from the lift cylinder  10  and is connected to the bottom chamber  10   a  of the lift cylinder  10 . The pipe K 4  connects the lift cylinder  10  and the hydraulic pump motor  11 . The pipe K 4  includes a pilot check valve  20 . The pilot check valve  20  serves as a second direction control valve that switches a flow direction of the hydraulic oil flowing in the second oil passage. As schematically shown in  FIG. 2 , the pilot check valve  20  of the present embodiment has a structure in which a main body accommodates a valve body  20   a  that includes a throttle oil passage  20   b . The throttle oil passage  20   b  connects the pipe K 4  arranged between the pilot check valve  20  and the bottom chamber  10   a  of the lift cylinder  10  and a spring chamber  20   c  accommodated in the main body. The throttle oil passage  20   b  is formed by a large diameter oil passage  20   d  that opens to the spring chamber  20   c  and a small diameter oil passage  20   e  that extends through from the circumferential surface of the valve body  20   a  toward the large diameter oil passage  20   d . The small diameter oil passage  20   e  has a small diameter compared to the large diameter oil passage  20   d.    
         [0037]    When the hydraulic pump motor  11  is activated, the hydraulic oil is discharged from the transmission opening  11   a , which serves as the outlet, and flows through the main pipe K. When receiving the pressure of the hydraulic oil, the valve body  20   a  moves. This opens the pilot check valve  20  and allows the hydraulic oil to flow to a passage located toward the lift cylinder  10  from the pilot check valve  20 . When deactivation of the hydraulic pump motor  11  stops the flow of the oil passage, the valve body  20   a  receives an urging force of a spring arranged in the spring chamber  20   c . This moves the valve body  20   a  and closes the pilot check valve  20 , which is open. Additionally, when a difference between the pressure of the pipe K 4  located toward the lift cylinder  10  from the pilot check valve  20  and the pressure of the spring chamber  20   c  reaches a predetermined pressure, the valve body  20   a  receives the pressure difference. This moves the valve body  20   a  and opens the pilot check valve  20 . The pilot check valve  20 , which is open, flows the hydraulic oil discharged from the bottom chamber  10   a  of the lift cylinder  10  to an oil passage located toward the main pipe K (hydraulic pump motor  11 ) from the pilot check valve  20 . More specifically, the pressure difference, which is used as a pressure for moving the valve body  20   a  (pilot pressure), opens the pilot check valve  20 . The pilot check valve  20  of the present embodiment forms an opening-closing unit that opens and closes the pipe K 4 , which serves as the second oil passage. 
         [0038]    The spring chamber  20   c  of the pilot check valve  20  is connected to a pipe K 5 , which serves as a third oil passage. The pipe K 5  includes an electromagnetic switch valve  22 , which serves as a switch valve, with a filter  21  arranged between the electromagnetic switch valve  22  and the spring chamber  20   c  of the pilot check valve  20 . The pipe K 5  is connected to the main pipe K that is connected to the transmission opening  11   a  of the hydraulic pump motor  11 . The pipe K 5  also serves as a return oil passage. More specifically, the hydraulic oil, which flows to the pipe K 5  from the pilot check valve  20 , passes through the electromagnetic switch valve  22  and returns to the transmission opening  11   a  of the hydraulic pump motor  11  through the main pipe K. 
         [0039]    The electromagnetic switch valve  22  may be shifted between two positions, namely, a first position  22   a  and a second position  22   b . When a solenoid is not excited, the electromagnetic switch valve  22  of the present embodiment is set at the first position  22   a  and allows the hydraulic oil to flow from the pipe K 5  to the main pipe K. When the solenoid is excited, the electromagnetic switch valve  22  of the present embodiment is set at the second position  22   b  and allows the hydraulic oil to bidirectionally flow between the pipe K 5  and the main pipe K. The electromagnetic switch valve  22  of the present embodiment is an on-off valve, which adjusts an open degree in accordance with the excitement (on) and non-excitement (off) of the solenoid. Thus, the electromagnetic switch valve  22  of the present embodiment differs from an electromagnetic proportional valve capable of adjusting the open degree in a non-stepped manner. 
         [0040]    In the present embodiment, the maximum open degrees of the electromagnetic switch valve  19 , the pilot check valve  20 , and the electromagnetic switch valve  22 , are each set as described below. In the description hereafter, the open degree of each of the electromagnetic switch valve  19  and the electromagnetic switch valve  22  become maximal when set at the second positions  19   b ,  22   b , respectively. The open degree of the pilot check valve  20  is maximal when the valve body  20   a  is open. In the present embodiment, the maximum open degree of the pilot check valve  20  is set to be larger than the maximum open degree of each of the electromagnetic switch valves  19 ,  22 . In other words, the maximum open degree of each of the electromagnetic switch valves  19 ,  22  is set to be smaller than the maximum open degree of the pilot check valve  20 . More specifically, the ratio of the maximum open degree of the electromagnetic switch valve  19  to the maximum open degree of the pilot check valve  20  is set to be in a range of 1:20 to 1:50. That is, the maximum open degree of the pilot check valve  20  is set to be in a range of 20 to 50 times larger than the maximum open degree of the electromagnetic switch valve  19 . The open degree of the electromagnetic switch valve  19  is set so that a value indicating a shock that occurs during a lowering operation is below a target value. The maximum open degree of the electromagnetic switch valve  22  is set to be the same as or larger than the maximum open degree of the electromagnetic switch valve  19 . In the hydraulic control mechanism of the present embodiment, the maximum open degree of the electromagnetic switch valve  19  corresponds to the maximum oil passage area of the first oil passage. The maximum open degree of the pilot check valve  20  corresponds to the maximum oil passage area of the second oil passage. Thus, the maximum oil passage area of the pipe K 1 , which includes the electromagnetic switch valve  19  and serves as the first oil passage, is smaller than the maximum oil passage area of the pipe K 4 , which includes the pilot check valve  20  and serves as the second oil passage. 
         [0041]    The structure of a controller S of the hydraulic control mechanism will now be described. 
         [0042]    The controller S is electrically connected to a potentiometer Lm that detects the amount of operation of the lift lever L. The controller S controls the rotation speed of the lift motor  12  based on a detection signal from the potentiometer Lm in accordance with the operation amount of the lift lever L. The controller S also controls the open degree of each of the electromagnetic switch valves  19 ,  22  during lifting and lowering operations. 
         [0043]    Additionally, the controller S is electrically connected to an inverter S 1 . Power is supplied to the lift motor  12  from a battery BT installed in the forklift via the inverter S 1 . Power generated with the lift motor  12  is stored in the battery BT via the inverter S 1 . The forklift of the present embodiment is of a battery type that travels by supplying power from the battery BT to a traveling motor, which serves as a motor. In the present embodiment, the controller S functions as an opening-closing unit that opens and closes the first oil passage and the second oil passage by performing open-close control. The controller S also functions as a measurement unit. 
         [0044]    The operation of the hydraulic control mechanism of the present embodiment will now be described. 
         [0045]    The operation for lifting the fork F will now be described. 
         [0046]    When lifting the fork F, the hydraulic oil is supplied to the bottom chamber  10   a  of the lift cylinder  10 . Thus, the controller S controls the rotation speeds of the hydraulic pump motor  11  and the lift motor  12  to perform lifting at a speed that is in accordance with the operation amount instructed with the lift lever L. The controller S also sets the electromagnetic switch valves  19 ,  22  at the first positions  19   a ,  22   a , respectively. Thus, the hydraulic oil, which is drawn from the oil tank  13  by the hydraulic pump motor  11 , flows through the main pipe K to the electromagnetic switch valve  19  and then the bottom chamber  10   a . That is, the direction in which the hydraulic oil flows is the direction in which the hydraulic oil flows from the oil tank  13  to the electromagnetic switch valve  19  and then from the electromagnetic switch valve  19  to the bottom chamber  10   a  of the lift cylinder  10 . The hydraulic oil, which is drawn from the oil tank  13  by the hydraulic pump motor  11 , flows to the pilot check valve  20  through the main pipe K. This opens the pilot check valve  20 . Consequently, the hydraulic oil flows to the bottom chamber  10   a . That is, the direction in which the hydraulic oil flows is the direction in which the hydraulic oil flows from the oil tank  13  to the pilot check valve  20  and then from the pilot check valve  20  to the bottom chamber  10   a  of the lift cylinder  10 . When the hydraulic oil enters the bottom chamber  10   a , the lift cylinder  10  is extended. This lifts the fork F. The hydraulic pump motor  11  functions as the hydraulic pump during the lifting operation. 
         [0047]    The operation for lowering the fork F will now be described with reference to  FIG. 3 . 
         [0048]    When lowering the fork F, the hydraulic oil is discharged from the bottom chamber  10   a  of the lift cylinder  10 . Thus, the controller S of the present embodiment opens the electromagnetic switch valve  19  first when the hydraulic pump motor  11  and the lift motor  12  are still (when the rotation speed of the pump is zero) (step S 10 ). More specifically, the controller S excites the solenoid of the electromagnetic switch valve  19  and shifts the position to the second position  19   b . Consequently, the hydraulic oil flows from the lift cylinder  10  to the hydraulic pump motor  11  through the pipe K 1  and then returns. That is, in step S 10 , the controller S opens the electromagnetic switch valve  19  so that the direction in which the hydraulic oil flows is the direction in which the hydraulic oil is allowed to flow from the lift cylinder  10  to the hydraulic pump motor  11 . The electromagnetic switch valve  19  of the present embodiment is set to have the maximum open degree that is sufficiently small. This limits the flow rate of the hydraulic oil returning to the hydraulic pump motor  11  through the pipe K 1 . In other words, a small amount of the hydraulic oil flows. Such a flow rate control of the hydraulic oil performed by the electromagnetic switch valve  19  gradually decreases the pressure difference of the electromagnetic switch valve  19  (pilot check valve  20 ) between an oil passage located toward the lift cylinder  10  from the electromagnetic switch valve  19  (pilot check valve  20 ) and an oil passage located toward the hydraulic pump motor  11  from the electromagnetic switch valve  19  (pilot check valve  20 ). The pressure difference decreases to a predetermined pressure difference or less. More specifically, the oil passage K 1  (oil passage K 4 ) includes a first portion between the electromagnetic switch valve  19  (pilot check valve  20 ) and the lift cylinder  10  and a second portion between the electromagnetic switch valve  19  (pilot check valve  20 ) and the hydraulic pump motor  11 . In the oil passage K 1  (oil passage K 4 ), a first pressure difference (second pressure difference) between the first portion and the second portion is gradually decreased to the predetermined pressure difference or less. The maximum open degree of the electromagnetic switch valve  19  is set to be small. Thus, the hydraulic oil does not suddenly stat flowing when the electromagnetic switch valve  19  opens. This reduces the shock that may be felt by an operator. 
         [0049]    At the same time as when the electromagnetic switch valve  19  opens, the controller S starts a timer used for measuring elapsed time (step S 20 ). Then, the controller S determines whether or not the timer, which was started in step S 20 , has reached a predetermined time X (step S 30 ). The time X is set to be short enough so that the operator does not feel a time lag from when the operator instructs a lowering operation to when the lowering operation actually starts. The time X of the present embodiment is set to be a fixed value defined in a range “from 0.1 to 0.5 seconds”. Additionally, the time X is set so that the pressure difference of the oil passage located toward the lift cylinder  10  from each of the electromagnetic switch valve  19  and the pilot check valve  20  and the oil passage located toward the hydraulic pump motor  11  from each of the electromagnetic switch valve  19  and the pilot check valve  20  is the predetermined pressure difference or less. The predetermined pressure difference or less only needs to be a pressure difference in which an operator of the lifting device (in the present embodiment, forklift) does not feel a shock. The controller S repeats the process of step S 30  when a determination result of step S 30  is NO. 
         [0050]    When the determination result of step S 30  is YES, the controller S opens the electromagnetic switch valve  22  (step S 40 ). More specifically, the controller S excites the solenoid of the electromagnetic switch valve  22  and shifts the position to the second position  22   b . The pilot check valve  20  freely opens when the hydraulic oil flows from the main pipe K, such as during the lifting operation. The pilot check valve  20  blocks the flow of the hydraulic oil from the bottom chamber  10   a , such as during the lowering operation. In this case, the application of the predetermined pilot pressure opens the pilot check valve  20 . 
         [0051]    Thus, when the controller S opens the electromagnetic switch valve  22 , the hydraulic oil between the bottom chamber  10   a  and the pilot check valve  20  sequentially flows to the spring chamber  20   c  and the electromagnetic switch valve  22  through the throttle oil passage  20   b  formed in the valve body  20   a  of the pilot check valve  20 . Then, the hydraulic oil returns to the main pipe K (hydraulic pump motor  11 ) through the pipe K 5 . A pressure drop may occur in the pilot check valve  20  when the hydraulic oil passes through the throttle oil passage  20   b . Such a pressure drop generates a pressure difference between an oil passage located toward the lift cylinder  10  from the throttle oil passage  20   b , which serves as an inflow side of the throttle oil passage  20   b , and an oil passage located toward the spring chamber  20   c  from the throttle oil passage  20   b , which serves as an outflow side of the throttle oil passage  20   b . More specifically, the pressure of the oil passage located toward the spring chamber  20   c  becomes lower than the pressure of the oil passage located toward the lift cylinder  10 . Thus, the pressure difference (second pressure difference) generated between the inflow side and the outflow side of the throttle oil passage  20   b  causes the valve body  20   a  to gradually open. Consequently, the hydraulic oil discharged from the bottom chamber  10   a  of the lift cylinder  10  directly flows to the main pipe K through the pipe K 4 . 
         [0052]    If the diameter (minimum diameter) of the small diameter oil passage  20   e , which forms the throttle oil passage  20   b , is too large relative to the maximum open degree of the electromagnetic switch valve  22 , the pressure difference would not be generated between the inflow side and the outflow side of the throttle oil passage  20   b . Thus, the valve body  20   a  would not open. If the diameter (minimum diameter) of the small diameter oil passage  20   e  is too small, the pressure difference would be too large between the inflow side and the outflow side of the throttle oil passage  20   b . Thus, the valve body  20   a  would quickly open. Thus, the diameter (minimum diameter) of the small diameter oil passage  20   e  is set to generate a pressure difference that opens the valve body  20   a  and to be suitable for the open degree of the electromagnetic switch valve  22 . 
         [0053]    At a timing when the pilot check valve  20  starts to open, the controller S controls the rotation speeds of the hydraulic pump motor  11  and the lift motor  12  so that the operation is performed at the speed instructed in accordance with the operation amount of the lift lever L. 
         [0054]    In such a control, when opening the pilot check valve  20 , which has the large maximum open degree, the pressure difference has been decreased by opening the electromagnetic switch valve  19 , which has the small maximum open degree. This limits generation of a shock caused by a sudden flow of the hydraulic oil when the pilot check valve  20  opens, that is, degreases a shock that may occur when the hydraulic oil flows due to the pressure difference between the oil passage located toward the lift cylinder  10  from the electromagnetic switch valve  19  (pilot check valve  20 ) and the oil passage located toward the hydraulic pump motor  11  from the electromagnetic switch valve  19  (pilot check valve  20 ). 
         [0055]    Then, the hydraulic oil discharged from the bottom chamber  10   a  of the lift cylinder  10  is drawn through the main pipe K into the transmission opening  11   a  of the hydraulic pump motor  11 . In this case, the transmission opening  11   a  functions as the inlet. The hydraulic pump motor  11  uses the hydraulic oil discharged from the bottom chamber  10   a  as driving power and operates as the hydraulic motor. Consequently, the lift motor  12  functions as the electric generator. Power generated with the lift motor  12  is stored in the battery BT via the inverter S 1 . More specifically, a regeneration operation is performed when lowering the fork F. The hydraulic oil, which serves as the driving power of the hydraulic pump motor  11 , flows from the lift cylinder  10  to the hydraulic pump motor  11  through the oil passages, that is, the pipe K 1  and the pipe K 4 , when the electromagnetic switch valve  19  and the pilot check valve  20  open, respectively. 
         [0056]    Accordingly, the present embodiment has the advantages described below. 
         [0057]    (1) During the lowering operation, the electromagnetic switch valve  19 , which has the small maximum open degree, opens first. This opens the oil passage between the lift cylinder  10  and the hydraulic pump motor  11 . Since the electromagnetic switch valve  19  has the small maximum open degree, the flow rate of the hydraulic oil flowing to the oil passage is limited. Thus, the hydraulic oil does not suddenly start flowing. Additionally, the opening of the electromagnetic switch valve  19  decreases the pressure difference between the lift cylinder  10  and the hydraulic pump motor  11 . After the oil passage opens between the lift cylinder  10  and the hydraulic pump motor  11 , the pilot check valve  20  having the large maximum open degree may open. In this case, if a predetermined condition is satisfied, the pressure difference has been already decreased. This limits the generation of a shock even when the hydraulic oil suddenly flows, thereby decreasing a shock that may occur when lowering the lifting material. 
         [0058]    (2) Additionally, when the lowering operation starts, the control for the lifting operation is not performed on the hydraulic pump motor  11 . This minimizes the time lag from when a lowering operation is instructed to when the lowering operation is actually performed. Consequently, the lifting material may be promptly operated. 
         [0059]    (3) During the lowering operation, the regeneration operation is performed by using the hydraulic oil discharged from the lift cylinder  10  as the driving power that drives the hydraulic pump motor  11  as the hydraulic motor. Thus, electric energy may be efficiently used. In the present embodiment, the maximum open degree of the pilot check valve  20  is set to be sufficiently large. Thus, the pressure drop is small when the hydraulic oil passes through the pilot check valve  20 . This provides a sufficient torque used for rotating the hydraulic pump motor  11  as the hydraulic motor. Consequently, electric energy may be efficiently obtained from the regeneration operation. 
         [0060]    (4) The difference in the maximum open degree between the electromagnetic switch valve  19  and the pilot check valve  20  is set to be large. This promptly operates the fork F while decreasing a shock that may occur when lowering the lifting material by controlling the timing for opening the electromagnetic switch valve  19  and the pilot check valve  20  without proportionally controlling open degrees of the valves. 
         [0061]    (5) The valve open degree of an electromagnetic proportional valve may be proportionally controlled. When such an electromagnetic proportional valve is employed, the pressure difference may be decreased by adjusting the open degree of the electromagnetic proportional valve without using the electromagnetic switch valve  19 , the pilot check valve  20 , and the electromagnetic switch valve  22 . That is, a shock that may occur during the lowering operation would be decreased. However, an electromagnetic proportional valve is expensive. Additionally, a current amplifier is needed to drive a proportional valve when an electromagnetic proportional valve is employed. Thus, the overall cost would increase. Moreover, the hydraulic control mechanism would be enlarged. Thus, the present embodiment, which uses no electromagnetic proportional valve, limits an increase in costs. 
         [0062]    (6) In particular, when a regeneration operation is performed during the lowering operation, the regeneration is more efficient when an on-off valve (electromagnetic switch valve  19 ) is employed than when an electromagnetic proportional valve is employed. Thus, the structure of the present embodiment may increase the efficiency of the regeneration operation while reducing a shock. 
         [0063]    (7) The timing for opening the pilot check valve  20  is time-managed. This eliminates a need for various kinds of sensors, which are needed when the timing for opening the valve is managed using pressure, flow rate, or the like. Thus, the structure and control may be simplified. 
         [0064]    (8) The electromagnetic switch valve  22  is used to control the opening of the pilot check valve  20 . More specifically, the electromagnetic switch valve  22  is the means for applying the pilot pressure to the pilot check valve  20 . This limits an enlargement of the device and an increase in costs compared to when an electromagnetic switch valve having a large maximum open degree is employed instead of the pilot check valve  20 . Additionally, there is no need to set the electromagnetic switch valve  22  to have a large maximum open degree. This reduces consumption of power needed for controlling the opening of the valve. 
       Second Embodiment 
       [0065]    A second embodiment of the present invention will now be described with reference to  FIG. 4 . In the embodiment described below, the same reference symbols are given to those components having the same structure as the embodiment that has been described. Such components will not be described in detail. 
         [0066]    The hydraulic control mechanism of the present embodiment includes the pipe K 4  serving as the second oil passage, which is arranged separately from the pipe K 1  and forms the passage through which the hydraulic oil is supplied to and discharged from the lift cylinder  10 . The pipe K 4  includes an electromagnetic switch valve  23 , which serves as the second direction control valve that switches a flow direction of the hydraulic oil in the second oil passage. When a solenoid is not excited, the electromagnetic switch valve  23  of the present embodiment is set at a first position  23   a  and allows the hydraulic oil to flow from the hydraulic pump motor  11  to the lift cylinder  10 . When the solenoid is excited, the electromagnetic switch valve  23  of the present embodiment is set at a second position  23   b  and allows the hydraulic oil to bidirectionally flow between the hydraulic pump motor  11  and the lift cylinder  10 . The electromagnetic switch valve  23  of the present embodiment is an on-off valve, which adjusts an open degree in accordance with the excitement (on) and non-excitement (off) of the solenoid. Thus, the electromagnetic switch valve  23  of the present embodiment differs from an electromagnetic proportional valve capable of adjusting the open degree in a non-stepped manner. The electromagnetic switch valve  23  of the present embodiment forms the opening-closing unit that opens and closes the pipe K 4 , which serves as the second oil passage. 
         [0067]    In the present embodiment, the maximum open degrees of the electromagnetic switch valve  19  and the electromagnetic switch valve  23  are each set as described below. The open degree of the electromagnetic switch valve  23  becomes maximal when set at the second position  23   b . In the present embodiment, the maximum open degree of the electromagnetic switch valve  23  is set to be larger than the maximum open degree of the electromagnetic switch valve  19 . In other words, the maximum open degree of the electromagnetic switch valve  19  is set to be smaller than the maximum open degree of the electromagnetic switch valve  23 . More specifically, the ratio of the maximum open degree of the electromagnetic switch valve  19  to the maximum open degree of the electromagnetic switch valve  23  is set to be in a range of 1:20 to 1:50. That is, the maximum open degree of the electromagnetic switch valve  23  is set to be in a range of 20 to 50 times larger than the maximum open degree of the electromagnetic switch valve  19 . In the hydraulic control mechanism of the present embodiment, the maximum open degree of the electromagnetic switch valve  19  corresponds to the maximum oil passage area of the first oil passage. The maximum open degree of the electromagnetic switch valve  23  corresponds to the maximum oil passage area of the second oil passage. 
         [0068]    The operation of the hydraulic control mechanism of the present embodiment will now be described. 
         [0069]    The operation of the hydraulic control mechanism of the present embodiment differs from the first embodiment in the control of the electromagnetic switch valve  23 . The contents of the control of the electromagnetic switch valve  19  are the same as the first embodiment. The controller S of the present embodiment also functions as the opening-closing unit that opens and closes the first oil passage and the second oil passage. 
         [0070]    The operation for lifting the fork F will now be described. 
         [0071]    The controller S controls the rotation speeds of the hydraulic pump motor  11  and the lift motor  12  so that the fork F is lifted at a speed that is in accordance with the operation amount instructed with the lift lever L. The controller S also sets the electromagnetic switch valves  19 ,  23  at the first positions  19   a ,  23   a , respectively. Thus, the hydraulic oil, which is drawn from the oil tank  13  by the hydraulic pump motor  11 , flows through the main pipe K to each of the electromagnetic switch valves  19 ,  23  and then the bottom chamber  10   a . That is, the direction in which the hydraulic oil flows is the direction in which the hydraulic oil flows from the oil tank  13  to each of the electromagnetic switch valves  19 ,  23  and then from each of the electromagnetic switch valves  19 ,  23  to the bottom chamber  10   a  of the lift cylinder  10 . When the hydraulic oil enters the bottom chamber  10   a , the lift cylinder  10  is extended. This lifts the fork F. 
         [0072]    The operation for lowering the fork F will now be described. 
         [0073]    The controller S opens the electromagnetic switch valve  19  first when the hydraulic pump motor  11  and the lift motor  12  are still (when the rotation speed of the pump is zero) (step S 10  of  FIG. 3 ). At the same time as when the electromagnetic switch valve  19  opens, the controller S starts the timer used for measuring elapsed time (step S 20  of  FIG. 3 ). 
         [0074]    When the timer reaches the predetermined time X (determined YES in step S 30  of  FIG. 3 ), the controller S opens the electromagnetic switch valve  23 . More specifically, the controller S excites the solenoid of the electromagnetic switch valve  23  and shifts the position to the second position  23   b . Consequently, the hydraulic oil flows from the lift cylinder  10  to the hydraulic pump motor  11  through the pipe K 1  and returns. That is, the controller S opens the electromagnetic switch valve  23  so that the direction in which the hydraulic oil flows is the direction in which the hydraulic oil is allowed to flow from the lift cylinder  10  to the hydraulic pump motor  11 . Additionally, at a timing when the electromagnetic switch valve  23  opens, the controller S controls the rotation speeds of the hydraulic pump motor  11  and the lift motor  12  so that the operation is performed at the speed instructed in accordance with the operation amount of the lift lever L. 
         [0075]    In the same manner as the first embodiment, in such a control, when opening the electromagnetic switch valve  23 , which has the large maximum open degree, the pressure difference has been decreased by opening the electromagnetic switch valve  19 , which has the small maximum open degree. This limits generation of a shock caused by a sudden flow of the hydraulic oil when the electromagnetic switch valve  23  opens, that is, decreases a shock that may occur when the hydraulic oil flows due to the pressure difference between the oil passage located toward the lift cylinder  10  from the electromagnetic switch valve  19  and the oil passage located toward the hydraulic pump motor  11  from the electromagnetic switch valve  19 . 
         [0076]    Then, the hydraulic oil discharged from the bottom chamber  10   a  of the lift cylinder  10  is drawn through the main pipe K into the transmission opening  11   a  of the hydraulic pump motor  11 . Thus, the hydraulic pump motor  11  operates as the hydraulic motor. Consequently, the regeneration operation is performed when lowering the fork F. The hydraulic oil, which serves as the driving power of the hydraulic pump motor  11 , flows from the lift cylinder  10  to the hydraulic pump motor  11  through the oil passages, that is, the pipe K 1  and the pipe K 4 , when the electromagnetic switch valve  19  and the electromagnetic switch valve  23  respectively open. 
         [0077]    The present embodiment has advantages (1) to (7) of the first embodiment. In the advantages of the present embodiment, the “pilot check valve  20 ” and the “electromagnetic switch valve  22 ” in advantages (1) to (7) of the first embodiment are replaced by the “electromagnetic switch valve  23 ”. 
       Third Embodiment 
       [0078]    A third embodiment of the present invention will now be described with reference to  FIG. 5 . 
         [0079]    In the hydraulic control mechanism of the present embodiment, an electromagnetic switch valve  25  is arranged in the pipe K 1 , which connects the bottom chamber  10   a  of the lift cylinder  10  and the hydraulic pump motor  11 . The electromagnetic switch valve  25  may be shifted between three positions, namely, a first position  25   a , a second position  25   b , and a third position  25   c . When neither a first solenoid  25   d  nor a second solenoid  25   e  is excited, the electromagnetic switch valve  25  of the present embodiment is set at the first position  25   a  and allows the hydraulic oil to flow from the hydraulic pump motor  11  to the lift cylinder  10 . When the first solenoid  25   d  is excited, the electromagnetic switch valve  25  of the present embodiment is set at the second position  25   b  and allows the hydraulic oil to bidirectionally flow between the hydraulic pump motor  11  and the lift cylinder  10 . When the second solenoid  25   e  is excited, the electromagnetic switch valve  25  of the present embodiment is set at the third position  25   c  and allows the hydraulic oil to bidirectionally flow between the hydraulic pump motor  11  and the lift cylinder  10 . The electromagnetic switch valve  25  of the present embodiment is an on-off valve, which adjusts an open degree in accordance with the excitement (on) and non-excitement (off) of the solenoid. Thus, the electromagnetic switch valve  25  of the present embodiment differs from an electromagnetic proportional valve capable of adjusting the open degree in a non-stepped manner. 
         [0080]    Further, the electromagnetic switch valve  25  of the present embodiment has different maximum open degrees between the second position  25   b  and the third position  25   c . More specifically, the maximum open degree of the third position  25   c  is set to be larger than the maximum open degree of the second position  25   b . In other words, the maximum open degree of the second position  25   b  is set to be smaller than the maximum open degree of the third position  25   c . The ratio of the maximum open degree of the second position  25   b  to the maximum open degree of the third position  25   c  is set to be in a range of 1:20 to 1:50. That is, the maximum open degree of the third position  25   c  is set to be in a range of 20 to 50 times larger than the maximum open degree of the second position  25   b . The relationship of the maximum open degree of the second position  25   b  and the maximum open degree of the third position  25   c  is the same as the relationship of the maximum open degrees of the electromagnetic switch valve  19  and the electromagnetic switch valve  22  of the first embodiment and the relationship of the maximum open degrees of the electromagnetic switch valve  19  and the electromagnetic switch valve  23  of the second embodiment. 
         [0081]    The hydraulic control mechanism of the present embodiment includes a first oil passage and a second oil passage. The first oil passage is formed by the pipe K 1  and connects the lift cylinder  10  and the hydraulic pump motor  11  via the electromagnetic switch valve  25  when set at the second position  25   b . The second oil passage is formed by the pipe K 1  and connects the lift cylinder  10  and the hydraulic pump motor  11  via the electromagnetic switch valve  25  when set at the third position  25   c . In the electromagnetic switch valve  25  of the hydraulic control mechanism of the present embodiment, the maximum open degree of the second position  25   b  is smaller than that of the third position  25   c . Thus, when configured in the above manner, the maximum oil passage area of the first oil passage is smaller than the maximum oil passage area of the second oil passage. The electromagnetic switch valve  25  forms an opening-closing unit that opens and closes each of the first oil passage and the second oil passage. The electromagnetic switch valve  25  of the present embodiment serves as the first direction control valve when set at the second position  25   b , and serves as the second direction control valve when set at the third position  25   c . Thus, the electromagnetic switch valve  25  includes both the first direction control valve and the second direction control valve. 
         [0082]    The operation of the hydraulic control mechanism of the present embodiment will now be described. 
         [0083]    The operation of the hydraulic control mechanism of the present embodiment differs from the first and second embodiments in that the electromagnetic switch valve  25  is controlled. The controller S of the present embodiment also functions as the opening-closing unit that opens and closes the first oil passage and the second oil passage. 
         [0084]    The operation for lifting the fork F will now be described. 
         [0085]    The controller S controls the rotation speeds of the hydraulic pump motor  11  and the lift motor  12  so that the fork F is lifted at a speed that is in accordance with the operation amount instructed with the lift lever L. The controller S also sets the electromagnetic switch valve  25  at the first position  25   a . Thus, the hydraulic oil, which is drawn from the oil tank  13  by the hydraulic pump motor  11 , flows through the main pipe K to the electromagnetic switch valve  25  and then to the bottom chamber  10   a . That is, the direction in which the hydraulic oil flows is the direction in which the hydraulic oil flows from the oil tank  13  to the electromagnetic switch valve  25  and then from the electromagnetic switch valve  25  to the bottom chamber  10   a  of the lift cylinder  10 . When the hydraulic oil enters the bottom chamber  10   a , the lift cylinder  10  is extended. This lifts the fork F. 
         [0086]    The operation for lowering the fork F will now be described. 
         [0087]    The controller S opens the electromagnetic switch valve  25  at the second position  25   b  when the hydraulic pump motor  11  and the lift motor  12  are still (when the rotation speed of the pump is zero). At the same time as when the electromagnetic switch valve  25  opens at the second position  25   b , the controller S starts the timer used for measuring the elapsed time. When the timer reaches the predetermined time X, the controller S shifts the electromagnetic switch valve  25  from the second position  25   b  to the third position  25   c . Thus, the electromagnetic switch valve  25  opens at the third position  25   c . In the hydraulic control mechanism of the present embodiment, the hydraulic oil flows from the lift cylinder  10  to the hydraulic pump motor  11  through the pipe K 1  and one of the second position  25   b  and the third position  25   c  of the electromagnetic switch valve  25 . This returns the hydraulic oil to the hydraulic pump motor  11 . That is, the controller S opens the electromagnetic switch valve  25  at one of the second position  25   b  and the third position  25   c  so that the direction in which the hydraulic oil flows is the direction in which the hydraulic oil is allowed to flow from the lift cylinder  10  to the hydraulic pump motor  11 . Additionally, at a timing when the electromagnetic switch valve  25  opens at the third position  25   c , the controller S controls the rotation speeds of the hydraulic pump motor  11  and the lift motor  12  so that the operation is performed at the speed instructed in accordance with the operation amount of the lift lever L. 
         [0088]    In the same manner as the first and second embodiments, in such a control, when opening the electromagnetic switch valve  25  at the third position  25   c , which has the large maximum open degree, the pressure difference has been decreased by opening the electromagnetic switch valve  25  at the second position  25   b , which has the small maximum open degree. This limits generation of a shock caused by a sudden flow of the hydraulic oil when the electromagnetic switch valve  25  opens at the third position  25   c , that is, decreases a shock that may occur when the hydraulic oil flows due to the pressure difference between the oil passage located toward the lift cylinder  10  from the electromagnetic switch valve  25  and the oil passage located toward the hydraulic pump motor  11  from the electromagnetic switch valve  25 . 
         [0089]    Then, the hydraulic oil discharged from the bottom chamber  10   a  of the lift cylinder  10  is drawn through the main pipe K into the transmission opening  11   a  of the hydraulic pump motor  11 . Thus, the hydraulic pump motor  11  operates as the hydraulic motor. Consequently, the regeneration operation is performed when lowering the fork F. The hydraulic oil, which serves as the driving power of the hydraulic pump motor  11 , flows from the lift cylinder  10  to the hydraulic pump motor  11  through the pipe K 1  when the electromagnetic switch valve  25  opens. 
         [0090]    The present embodiment has the advantages described below in addition to advantages (1) to (7) of the first embodiment. In the advantages of the present embodiment, the “electromagnetic switch valve  19 ” and the “pilot check valve  20 ” in advantages (1) to (7) of the first embodiment are replaced by the “electromagnetic switch valve  25 ”. 
         [0091]    (9) The pipe K 1  includes the electromagnetic switch valve  25  capable of opening at the second position  25   b  and the third position  25   c , which have different maximum open degrees. More specifically, the single electromagnetic switch valve  25  is arranged in the oil passage connecting the lift cylinder  10  and the hydraulic pump motor  11  to control the amount of the hydraulic oil flowing through the pipe K 1 . This simplifies the hydraulic control mechanism. Use of the single electromagnetic switch valve  25  also simplifies the piping connecting the lift cylinder  10  and the hydraulic pump motor  11 . 
       Fourth Embodiment 
       [0092]    A fourth embodiment of the present invention will now be described with reference to  FIG. 6 . 
         [0093]    The hydraulic control mechanism of the present embodiment includes an electromagnetic switch valve  26  arranged in the pipe K 1 , which connects the bottom chamber  10   a  of the lift cylinder  10  and the hydraulic pump motor  11 . The electromagnetic switch valve  26  serves as the first direction control valve, which switches a flow direction of the hydraulic oil in the first oil passage. The electromagnetic switch valve  26  of the present embodiment is a four-port valve and arranged in the pipe K 5 , which connects the main pipe K and the oil tank  13 , in addition to the pipe K 1 . The electromagnetic switch valve  26  may be shifted between two positions, namely, a first position  26   a  and a second position  26   b . When a solenoid is not excited, the electromagnetic switch valve  26  of the present embodiment is set at the first position  26   a  and allows the hydraulic oil to flow in one direction. When the solenoid is excited, the electromagnetic switch valve  26  of the present embodiment is set at the second position  26   b  and allows the hydraulic oil to flow in two directions. The electromagnetic switch valve  26  of the present embodiment is an on-off valve, which adjusts an open degree in accordance with the excitement (on) and non-excitement (off) of the solenoid. Thus, the electromagnetic switch valve  26  of the present embodiment differs from an electromagnetic proportional valve capable of adjusting the open degree in a non-step manner. 
         [0094]    Additionally, the hydraulic control mechanism of the present embodiment includes the pilot check valve  20  arranged in the pipe K 4 , which connects the bottom chamber  10   a  of the lift cylinder  10  and the hydraulic pump motor  11 . The spring chamber  20   c  of the pilot check valve  20  is connected to a pressure compensation valve  27 , which serves as a switch valve, via the filter  21 . The specific configuration of the pilot check valve  20  is as illustrated in the first embodiment with reference to  FIG. 2 . Thus, the configuration is the same as the first embodiment. 
         [0095]    The pressure compensation valve  27  may be shifted between two positions, namely, a first position  27   a  and a second position  27   b . The pressure compensation valve  27  is connected to the pipe K 5  located between the main pipe K and the electromagnetic switch valve  26  and the pipe K 5  located between the electromagnetic switch valve  26  and the oil tank  13 . The pressure compensation valve  27  is normally set at the first position  27   a . When the pressure of the pipe K 5  increases between the electromagnetic switch valve  26  and the oil tank  13 , the pressure compensation valve  27  shifts from the first position  27   a  to the second position  27   b . When set at the first position  27   a , the pressure compensation valve  27  allows the hydraulic oil to flow to the pipe K 5  located between the main pipe K and the electromagnetic switch valve  26 . When set at the second position  27   b , the pressure compensation valve  27  allows the hydraulic oil to flow in two directions. 
         [0096]    In the present embodiment, the maximum open degree of each of the electromagnetic switch valve  26  and the pilot check valve  20  is set as described below. In the description hereafter, the open degree of the electromagnetic switch valve  26  becomes maximal when set at the second position  26   b . Also, the open degree of the pilot check valve  20  is maximal when the valve body  20   a  is open. In the present embodiment, the maximum open degree of the pilot check valve  20  is set to be larger than the maximum open degree of the electromagnetic switch valve  26 . In other words, the maximum open degree of the electromagnetic switch valve  26  is set to be smaller than the maximum open degree of the pilot check valve  20 . More specifically, the ratio of the maximum open degree of the electromagnetic switch valve  26  to the maximum open degree of the pilot check valve  20  is set to be in a range of 1:20 to 1:50. That is, the maximum open degree of the pilot check valve  20  is set to be in a range of 20 to 50 times larger than the maximum open degree of the electromagnetic switch valve  26 . The relationship of the maximum open degree of the electromagnetic switch valve  26  and the maximum open degree of the pilot check valve  20  is the same as the relationship of the maximum open degrees of the electromagnetic switch valve  19  and the pilot check valve  20  of the first embodiment. 
         [0097]    In the hydraulic control mechanism of the present embodiment, the maximum open degree of the electromagnetic switch valve  26  corresponds to the maximum oil passage area of the first oil passage. The maximum open degree of the pilot check valve  20  corresponds to the maximum oil passage area of the second oil passage. Thus, the pipe K 1 , which includes the electromagnetic switch valve  26  and serves as the first oil passage, has the maximum oil passage area that is smaller than the maximum oil passage area of the pipe K 4 , which includes the pilot check valve  20  and serves as the second oil passage. In the same manner as the first embodiment, the present embodiment includes the opening-closing unit formed by the electromagnetic switch valve  26 , which opens and closes the pipe K 1  serving as the first oil passage, the pilot check valve  20 , which opens and closes the pipe K 4  serving as the second oil passage, and the controller S, which controls the opening and closing. 
         [0098]    The operation of the hydraulic control mechanism of the present embodiment will now be described. 
         [0099]    The operation for lifting the fork F will now be described. 
         [0100]    The controller S controls the rotation speeds of the hydraulic pump motor  11  and the lift motor  12  to perform lifting at a speed that is in accordance with the operation amount instructed with the lift lever L. The controller S also sets the electromagnetic switch valve  26  at the first position  26   a . Thus, the hydraulic oil, which is drawn from the oil tank  13  by the hydraulic pump motor  11 , flows through the main pipe K to the electromagnetic switch valve  26  and then the bottom chamber  10   a . That is, the direction in which the hydraulic oil flows is the direction in which the hydraulic oil flows from the oil tank  13  to the electromagnetic switch valve  26  and then from the electromagnetic switch valve  26  to the bottom chamber  10   a  of the lift cylinder  10 . When the hydraulic oil enters the bottom chamber  10   a , the lift cylinder  10  is extended. This lifts the fork F. 
         [0101]    The operation for lowering the fork F will now be described. 
         [0102]    When the hydraulic pump motor  11  and the lift motor  12  are still (when the rotation speed of the pump is zero), the electromagnetic switch valve  26  is set at the first position  26   a . The hydraulic oil does not flow from the bottom chamber  10   a  of the lift cylinder  10  to the pipe K 1 . Additionally, the pressure compensation valve  27  is set at the first position  27   a . This connects the bottom chamber  10   a  of the lift cylinder  10  and a pipe K 6  of the pressure compensation valve  27  via the throttle oil passage  20   b , which includes the small diameter oil passage  20   e  of the pilot check valve  20 . Thus, the pressure of the pipe K 6  is the same as the pressure of the bottom chamber  10   a . The pressure of the pipe K 6  sets the pressure compensation valve  27  at the first position  27   a . The hydraulic oil does not flow from the pipe K 6  to the pipe K 5 . 
         [0103]    When the lowering operation is instructed, the controller S opens the electromagnetic switch valve  26  at the second position  26   b . At same time as when the electromagnetic switch valve  26  opens at the second position  26   b , the controller S starts the timer used for measuring elapsed time. When the electromagnetic switch valve  26  is open at the second position  26   b , the hydraulic oil of the bottom chamber  10   a  passes through the electromagnetic switch valve  26 , the maximum open degree of which is set to be small. This increases the pressure of the oil passage located toward the hydraulic pump motor  11  from the electromagnetic switch valve  26 , thereby gradually decreasing the pressure difference at the inflow side and the outflow side of the electromagnetic switch valve  26  set at the second position  26   b . Consequently, the pressure difference decreases to the predetermined pressure difference or less. The maximum open degree of the electromagnetic switch valve  26  is set to be small. Thus, the hydraulic oil does not suddenly start flowing when the electromagnetic switch valve  26  opens. This reduces a shock that may be felt by an operator. 
         [0104]    When the electromagnetic switch valve  26  opens at the second position  26   b , the pressure of the pipe K 1  increases. This increases the pressure of the pipe K 5 , which is also open via the electromagnetic switch valve  26 . The increased pressure of the pipe K 5  triggers a shift of the pressure compensation valve  27  from the first position  27   a  to the second position  27   b . Thus, when the pressure difference between the pipe K 5  and the pipe K 6  decreases to the fixed value or less, the pressure compensation valve  27  shifts to the second position  27   b . When the pressure compensation valve  27  shifts to the second position  27   b , the hydraulic oil flows to the pipe K 5  through the throttle oil passage  20   b , which includes the small diameter oil passage  20   e  of the pilot check valve  20 . Then, a pressure drop occurs in the small diameter oil passage  20   e . This pushes the valve body  20   a  of the pilot check valve  20  in the direction in which the pipe K 4  opens. Consequently, the pilot check valve  20  opens. That is, the pressure drop that occurs when the hydraulic oil passes through the throttle oil passage  20   b  generates a pressure difference between the oil passage located toward the lift cylinder  10 , which serves as the inflow side of the throttle oil passage  20   b , and the oil passage located toward the spring chamber  20   c , which serves as the outflow side of the throttle oil passage  20   b . More specifically, the pressure of the spring chamber  20   c  is lower than the pressure of the oil passage located toward the lift cylinder  10  from the pilot check valve  20 . Thus, the pressure difference generated between the inflow side and the outflow side of the throttle oil passage  20   b  causes the valve body  20   a  to gradually open. Consequently, the hydraulic oil discharged from the bottom chamber  10   a  of the lift cylinder  10  directly flows to the main pipe K through the pipe K 4 . 
         [0105]    When a value measured by the timer reaches a fixed value, the controller S controls the rotation speeds of the hydraulic pump motor  11  and the lift motor  12  to perform lifting at a speed that is in accordance with the operation amount instructed with the lift lever L. In the hydraulic control mechanism of the present embodiment, the time when the pilot check valve  20  opens is calculated in advance through simulations. Then, the fixed value described above is set to be larger than or equal to the calculated value. The fixed value is also the time when the pressure difference between the oil passage located toward the lift cylinder  10  from the pilot check valve  20  and the oil passage located toward the hydraulic pump motor  11  from the pilot check valve  20  decreases to the predetermined pressure difference or less. 
         [0106]    In such a control, when opening the pilot check valve  20 , which has the large maximum open degree, the pressure difference has been decreased by opening the electromagnetic switch valve  26 , which has the small maximum open degree. This limits generation of a shock caused by a sudden flow of the hydraulic oil when the pilot check valve  20  opens, that is, decreases a shock that may occur when the hydraulic oil flows due to the pressure difference between the oil passage located toward the lift cylinder  10  and the oil passage located toward the hydraulic pump motor  11  from the electromagnetic switch valve  26 . 
         [0107]    Then, the hydraulic oil discharged from the bottom chamber  10   a  of the lift cylinder  10  is drawn through the main pipe K into the transmission opening  11   a  of the hydraulic pump motor  11 . In this case, the transmission opening  11   a  functions as the inlet. The hydraulic pump motor  11  uses the hydraulic oil discharged from the bottom chamber  10   a  as driving power and operates as the hydraulic motor. Consequently, the lift motor  12  functions as the electric generator. Power generated with the lift motor  12  is stored in the battery BT via the inverter S 1 . More specifically, a regeneration operation is performed when lowering the fork F. The hydraulic oil, which serves as the driving power of the hydraulic pump motor  11 , flows from the lift cylinder  10  to the hydraulic pump motor  11  through the oil passages, that is, the pipe K 1  and the pipe K 4 , when the electromagnetic switch valve  26  and the pilot check valve  20  respectively open. 
         [0108]    The present embodiment has the advantages described below in addition to advantages (1) to (8) of the first embodiment. In the advantages of the present embodiment, the “electromagnetic switch valve  19 ” and the “electromagnetic switch valve  22 ” in advantages (1) to (8) of the first embodiment are replaced by the “electromagnetic switch valve  26 ” and the “pressure compensation valve  27 ”, respectively. 
         [0109]    (10) The pressure compensation valve  27  shifts between the first position  27   a  and the second position  27   b  in accordance with the pressure of the pipe K 5 . The pressure compensation valve  27  controls the opening and closing of the pilot check valve  20 . Thus, the electromagnetic switch valve  26  is a single direction control valve the opening and closing of which is controlled by the controller S. This simplifies the hydraulic control mechanism. Also, use of the single electromagnetic switch valve  26  limits an increase in costs of the hydraulic control mechanism. 
         [0110]    Each embodiment may be modified as follows. 
         [0111]    In the first to the third embodiments, at the same time as when the electromagnetic switch valves  22 ,  23 ,  25  open, the hydraulic pump motor  11  and the lift motor  12  may be operated at a speed that is in accordance with the operation amount instructed with the lift lever L. 
         [0112]    In the first and the second embodiments, after the electromagnetic switch valve  19  opens, the electromagnetic switch valves  22 ,  23  may open when a condition is satisfied. The condition includes the flow rate of the hydraulic oil flowing to the hydraulic pump motor  11  and the decrease of the pressure difference between the inflow side and the outflow side of the electromagnetic switch valve  19 . In the third embodiment, after the electromagnetic switch valve  25  shifts to the second position  25   b , the electromagnetic switch valve  25  may shift to the third position  25   c  when a condition is satisfied. The condition includes the flow rate of the hydraulic oil flowing to the hydraulic pump motor  11  and the decrease of the pressure difference between the inflow side and the outflow side of the electromagnetic switch valve  25 . 
         [0113]    Each of the embodiments may be configured so that the electromagnetic switch valves  19 ,  22 ,  23 ,  25 ,  26  block the oil passage between the lift cylinder  10  and the hydraulic pump motor  11  when set at the first positions  19   a ,  22   a ,  23   a ,  25   a ,  26   a.    
         [0114]    In the first and the fourth embodiments, the throttle oil passage  20   b  formed in the valve body  20   a  may have any shape and arrangement. 
         [0115]    In the first embodiment, the pipe K 5  may be connected to the discharge pipe K 3  so that the hydraulic oil passing through the electromagnetic switch valve  22  returns to the oil tank  13 . 
         [0116]    The application of the hydraulic control mechanism of each embodiment is not limited to a forklift. The hydraulic control mechanism may be applied to an apparatus that performs lowering operation under its weight (e.g., hydraulic elevator). 
       DESCRIPTION OF REFERENCE SYMBOLS 
       [0000]    
       
         
           
               10  lift cylinder 
               11  hydraulic pump motor 
               19 ,  22 ,  23 ,  25 ,  26  electromagnetic switch valve 
               20  pilot check valve 
               20   a  valve body 
               20   b  throttle oil passage 
               27  pressure compensation valve 
             F fork 
             K 1 , K 4 , K 5  pipe 
             S controller 
             X time